Durability and performance coupling test device and method under acceleration condition of refrigeration compressor

Abstract

The invention relates to the technical field of compressors, and discloses a durability and performance coupling test device and method for a refrigeration compressor under an acceleration condition. The device comprises a refrigerant circulation assembly, an electromagnetic valve assembly, a controller and a data acquisition assembly. The refrigerant circulation assembly comprises a condenser, a liquid storage device, a subcooler and a calorimeter which are connected in sequence, an inlet of the condenser is connected with the exhaust end of the tested compressor, an outlet of the calorimeter is connected with the suction end of the tested compressor, and a loop for performance testing is formed; an inlet of the mixing heat exchanger is connected to a gas conveying pipeline in front of an inlet of the condenser through a gas inlet branch and connected to a liquid conveying pipeline behind an outlet of the subcooler through a liquid inlet branch. An outlet of the mixing heat exchanger is connected with an air suction end of the tested compressor to form a loop for an endurance test; the controller adjusts the communication state of the pipeline by controlling the plurality of electromagnetic valves so as to realize test state switching; the data acquisition assembly is used for acquiring flow, temperature and pressure data during a test. According to the invention, rapid switching between performance and endurance tests can be realized.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, in particular to a device and method for testing the durability and performance coupling of refrigeration compressors under accelerated conditions. Background Art

[0002] The compressor is a core component in an air conditioning system. Its performance and durability directly affect the system's operating efficiency and service life. To fully evaluate a compressor, two tests are typically required: performance testing and durability testing.

[0003] In existing technology, performance testing typically uses the "flow meter method," which routes the entire refrigerant cycle through a calorimeter and calculates the compressor's cooling capacity based on parameters such as flow rate and temperature. This method offers high test accuracy, but requires all components to be involved in the cycle, resulting in high energy consumption. Durability testing typically uses the "mixer method," which achieves circulation by mixing hot and cold refrigerants, thereby reducing energy consumption. However, this method cannot directly obtain highly accurate performance parameters.

[0004] In traditional test benches, performance test devices and durability test devices are often separated. When switching between the two test modes, the pipeline needs to be significantly modified or manually disassembled and assembled, which is complicated to operate, has low switching efficiency, and is prone to leakage risks. Or although the two devices are in the same system, the flow meters and other components used in the performance test are high-precision sensors, which are generally not suitable for 24-hour work systems and conflict with the durability test. Therefore, the existing technology urgently needs a compressor performance and durability coupling test device with integrated structure and convenient switching. It can realize the rapid conversion of the two test modes in the same pipeline system through simple control switching, while ensuring the accuracy of the performance test and the energy saving and service life of the durability test. Summary of the Invention

[0005] In order to solve the technical problems in the prior art that it is impossible to quickly switch between compressor performance test and durability test and the test state is difficult to maintain consistency, the present invention provides a durability and performance coupling test device and method for refrigeration compressors under accelerated conditions.

[0006] To achieve the above object, the present invention provides the following technical solutions:

[0007] The invention discloses a device for testing the durability and performance coupling of a refrigeration compressor under accelerated conditions, comprising a refrigerant circulation component, a solenoid valve component, a controller and a data acquisition component.

[0008] The refrigerant circulation assembly includes a condenser, a liquid accumulator, a subcooler, and a calorimeter connected in sequence. The inlet of the condenser is connected to the exhaust end of the tested compressor, and the outlet of the calorimeter is connected to the suction end of the tested compressor, forming a first refrigerant circulation loop for performance testing. The refrigerant circulation assembly also includes a mixing heat exchanger. The inlet of the mixing heat exchanger is connected to the air supply pipeline before the inlet of the condenser through an air inlet branch, and to the liquid supply pipeline after the outlet of the subcooler through a liquid inlet branch. The outlet of the mixing heat exchanger is connected to the suction end of the tested compressor, forming a second refrigerant circulation loop for durability testing.

[0009] The solenoid valve assembly includes a plurality of solenoid valves arranged on the pipeline;

[0010] The controller is used to adjust the pipeline connectivity by controlling multiple solenoid valves, thereby achieving state switching between performance test and endurance test. During the performance test, the refrigerant discharged from the test compressor passes through the condenser, liquid receiver, subcooler, and calorimeter for heat exchange in sequence before returning to the test compressor. During the endurance test, part of the refrigerant discharged from the test compressor enters the hybrid heat exchanger through the air inlet branch, and the other part passes through the condenser, liquid receiver, and subcooler and then enters the hybrid heat exchanger through the liquid inlet branch. The two refrigerants exchange heat in the hybrid heat exchanger before returning to the test compressor.

[0011] The data acquisition component is used to collect the flow, temperature and pressure data of the refrigerant in multiple sections of pipelines during performance and durability tests.

[0012] As a further improvement of the above solution, the test device also includes: a regulating valve assembly.

[0013] The regulating valve assembly includes a regulating valve, a second regulating valve and an expansion regulating valve;

[0014] The solenoid valve assembly includes solenoid valve 1, solenoid valve 2, solenoid valve 3, solenoid valve 4, solenoid valve 5, and solenoid valve 6;

[0015] The data acquisition component includes flow meter 1, flow meter 2, temperature and pressure acquisition module 1, temperature and pressure acquisition module 2, temperature and pressure acquisition module 3, temperature and pressure acquisition module 4 and temperature and pressure acquisition module 5;

[0016] Among them, solenoid valve 1 is arranged on the pipeline between the exhaust end of the test compressor and the condenser, and temperature and pressure acquisition module 1 is arranged on the pipeline between the exhaust end of the test compressor and solenoid valve 1; solenoid valve 2, flowmeter 1 and expansion regulating valve are arranged in sequence on the pipeline between the outlet of the subcooler and the inlet of the calorimeter, and temperature and pressure acquisition module 2 is arranged on the pipeline between flowmeter 1 and expansion regulating valve; solenoid valve 3 and flowmeter 2 are arranged in sequence on the pipeline between the outlet of the calorimeter and the suction end of the test compressor, and temperature and pressure acquisition module 3 is arranged on the pipeline between the outlet of the calorimeter and solenoid valve 3, and temperature and pressure acquisition module 4 is arranged on the pipeline between flowmeter 2 and the suction end of the test compressor; solenoid valve 4 and regulating valve are arranged in sequence on the air inlet branch, and solenoid valve 5 and regulating valve 2 are arranged in sequence on the liquid inlet branch; the outlet of the mixing heat exchanger is connected to the pipeline between flowmeter 2 and temperature and pressure acquisition module 4 through solenoid valve 6, and temperature and pressure acquisition module 5 is arranged on the pipeline between the outlet of the mixing heat exchanger and solenoid valve 6.

[0017] As a further improvement of the above solution, the regulating valve assembly further includes an oil regulating valve;

[0018] The solenoid valve assembly further includes a solenoid valve seven, a solenoid valve eight, a solenoid valve nine and a solenoid valve ten;

[0019] The data acquisition component also includes a temperature acquisition module;

[0020] The test device further includes an oil circulation component.

[0021] The oil circulation assembly includes an oil separator, an oil cooler and an oil heater; the refrigerant inlet and refrigerant outlet of the oil separator are connected in parallel to the pipelines at both ends of the solenoid valve one through solenoid valve seven and solenoid valve eight respectively; the oil outlet of the oil separator is divided into two oil outlet paths, of which the first oil outlet path is connected to the suction end of the test compressor through solenoid valve nine, oil cooler, oil heater, oil regulating valve and temperature acquisition module in sequence, and the first oil outlet path is used to regulate the temperature and flow of the recovered oil, and the second oil outlet path is directly connected to the suction end of the test compressor through solenoid valve ten.

[0022] As a further improvement to the above solution, the controller implements the following control strategy during the performance test:

[0023] Open solenoid valve seven, solenoid valve eight and solenoid valve nine, and close solenoid valve one and solenoid valve ten, so that the refrigerant discharged from the test compressor passes through the oil separator and recovers the oil to the test compressor through the first oil outlet; open solenoid valve two and solenoid valve three, and close solenoid valve four, solenoid valve five and solenoid valve six to form a first refrigerant circulation loop and perform simulated load heat exchange on the refrigerant output from the subcooler through the calorimeter.

[0024] As a further improvement to the above solution, during the durability test, the controller determines whether the durability test requires the intervention of the oil separator and executes the following control strategy:

[0025] When intervention is required: open solenoid valve 1 and solenoid valve 10, and close solenoid valve 7, solenoid valve 8, and solenoid valve 9, so that the refrigerant discharged from the test compressor passes through the oil separator and recovers the oil to the test compressor through the second oil outlet; open solenoid valve 4, solenoid valve 5, and solenoid valve 6, and close solenoid valve 2 and solenoid valve 3 to form a second refrigerant circulation loop and mix the refrigerants from the air inlet branch and the liquid inlet branch through the mixing heat exchanger;

[0026] When no intervention is required: open solenoid valve one, and close solenoid valves seven, eight, nine and ten, so that the refrigerant discharged from the test compressor bypasses the oil separator; open solenoid valves four, five and six, and close solenoid valves two and three to form a second refrigerant circulation loop and mix the oil-containing refrigerants from the air inlet branch and the liquid inlet branch through a mixing heat exchanger.

[0027] As a further improvement of the above scheme, the solenoid valve assembly also includes a solenoid valve eleven; one end of the solenoid valve eleven is connected to the pipeline between the temperature and pressure acquisition module five and the solenoid valve six, and the other end is connected to the enthalpy increase interface of the test compressor with the air replenishment and enthalpy increase function.

[0028] As a further improvement to the above solution, for the tested compressor with the air-injection and enthalpy-increasing function, the controller implements the following control strategy during the performance test:

[0029] Open solenoid valve seven, solenoid valve eight and solenoid valve nine, and close solenoid valve one and solenoid valve ten, so that the refrigerant discharged from the test compressor passes through the oil separator and recovers the oil to the test compressor through the first oil outlet; open solenoid valve two, solenoid valve three, solenoid valve four, solenoid valve five and solenoid valve eleven, and close solenoid valve six, so that on the basis of forming the first refrigerant circulation loop, the air inlet branch and the liquid inlet branch are kept open, so that the mixing heat exchanger transports refrigerant to the enthalpy increase interface to form an air replenishment and enthalpy increase circulation loop.

[0030] As a further improvement to the above scheme, when conducting a performance test on a test compressor with an air replenishment and enthalpy increase function, among all the refrigerants returning to the suction port of the test compressor, the refrigerant output by the calorimeter accounts for 75%-90%, and the refrigerant output by the mixing heat exchanger accounts for 10%-25%.

[0031] The present invention also discloses a coupled test method for durability and performance of a refrigeration compressor under accelerated conditions, which is applied to the test device described above; the coupled test method comprises the following steps:

[0032] Step 1: Obtain the operating parameters of the test compressor under the set actual operating conditions and the accelerated operating conditions of the endurance test respectively; the operating parameters include the compressor suction and exhaust temperature, suction and exhaust pressure, and suction specific volume;

[0033] Step 2: Calculate the acceleration factor σ between the actual operating condition and the accelerated condition based on the operating parameters under different operating conditions:

[0034] σ=(ΔP1 / ΔP0) a (v1 / v0) b ·exp(c(P 1D / P 0D )(1 / T0-1 / T1))

[0035] Wherein, ΔP1 is the ratio of the exhaust pressure to the suction pressure of the test compressor under acceleration conditions, ΔP0 is the ratio of the exhaust pressure to the suction pressure of the test compressor under actual operating conditions, and the unit is kPa / kPa; v1 is the suction specific volume of the test compressor under acceleration conditions, and v0 is the suction specific volume of the test compressor under actual operating conditions, and the unit is kg / m 3 ; T1 is the exhaust temperature of the tested compressor under accelerated working conditions, T0 is the exhaust temperature of the tested compressor under actual operating conditions, the unit is Kelvin; P 1D and P 0D are the exhaust pressures of the tested compressor under actual operating conditions and accelerated conditions, respectively; a, b, and c are the pressure conversion coefficient, specific volume conversion coefficient, and comprehensive conversion coefficient of the accelerated fatigue test, respectively; exp(·) is the natural exponential function;

[0036] Step 3: Obtain the designed service life of the test compressor and divide it by the acceleration factor σ to obtain the durability test time of the test compressor;

[0037] Step 4. Divide the durability test into multiple stages according to the duration of the durability test. Before the start of the durability test in each stage, conduct a performance test first. Then, adjust the pipeline connectivity status through the controller to conduct the durability test without stopping the machine, so as to conduct tests in all stages in turn and record the performance-related data and durability-related data during the test.

[0038] As a further improvement of the above scheme, the performance-related data include the cooling capacity, energy efficiency ratio, circulating refrigerant flow, suction and exhaust temperature, suction and exhaust pressure and motor temperature of the test compressor; the durability-related data include the suction and exhaust temperature, suction and exhaust pressure, compressor power and ambient temperature of the test compressor.

[0039] Compared with the prior art, the present invention has the following beneficial effects:

[0040] 1. The present invention integrates the performance test circuit and the durability test circulation circuit into the same set of refrigerant circulation devices. Through reasonable pipeline layout and combined control of electric valves, rapid switching of the two test modes on the same device is achieved, avoiding the disadvantages of frequent pipeline modification when using different test devices, saving equipment space and reducing construction costs. In the performance test mode, all the refrigerant flows through the calorimeter, which can accurately measure the cooling capacity or heating capacity of the compressor; in the durability test mode, the refrigerant is circulated through hot and cold mixing, which greatly reduces the energy consumption of the system. Since both tests are carried out in the same closed cycle, not only the risk of leakage caused by switching or disassembly is reduced, but also the safety and stability of the system operation are improved. At the same time, the piping and control design of the device can adapt to the testing requirements of compressors of different types and different refrigerants, and has good versatility and scalability.

[0041] 2. The test device of this invention maintains the compressor's operating condition to the greatest extent possible after a single installation, preventing variations in operating parameters such as oil quality and moisture content, thereby providing a higher degree of assurance for test accuracy. Switching between performance and endurance testing is instantaneous, effectively maintaining the temperature, thermal expansion conditions, and lubricant status of each compressor component, ensuring maximum test continuity and consistency. This design enables a comprehensive assessment of compressor reliability and the impact of endurance testing on performance, providing a reliable test basis for compressor development and optimization.

[0042] 3. The test device of the present invention can use high-precision flow meters and other sensors to achieve accurate measurement during the performance test stage, and these sensors can be shut down after switching to the endurance test, thereby meeting the accuracy requirements of the performance test and avoiding the reduction in life of high-precision sensors caused by long-term continuous operation, reducing maintenance and replacement costs, and improving the overall operating efficiency of the device.

[0043] 4. The coupling test method of the present invention obtains key parameters under actual operating conditions and accelerated conditions, scientifically calculates the acceleration factor, thereby reasonably shortening the durability test duration and significantly reducing test time and energy consumption. At the same time, a mode of alternating staged performance and durability tests is adopted to achieve seamless switching without stopping the machine, ensuring stable and consistent test conditions, and improving test efficiency and data reliability. This method, combined with the energy-saving hybrid heat exchanger durability test system, further reduces the energy consumption of long-term durability tests, meeting the requirements of efficient and low-consumption compressor performance and durability coupling evaluation. BRIEF DESCRIPTION OF THE DRAWINGS

[0044] Figure 1 Schematic diagram of the overall structure of the compressor performance and durability coupling test device in an embodiment of the present invention.

[0045] Figure 2 for Figure 1 Schematic diagram of the piping connectivity status of the test device during performance testing.

[0046] Figure 3 for Figure 1 Schematic diagram of the pipe connection status of the test device during the durability test.

[0047] Figure 4 for Figure 1 Schematic diagram of the piping connection status of the test device during the heat pump operating performance test.

[0048] Figure 5 Flowchart of the durability and performance coupling test method in Example 1 of the present invention.

[0049] In the figure: 1, tested compressor; 101, enthalpy increase interface; 21, condenser; 22, liquid receiver; 23, subcooler; 24, calorimeter; 25, mixing heat exchanger; 31, solenoid valve 1; 32, solenoid valve 2; 33, solenoid valve 3; 34, solenoid valve 4; 35, solenoid valve 5; 36, solenoid valve 6; 37, solenoid valve 7; 38, solenoid valve 8; 39, solenoid valve 9; 310, solenoid valve 10; 311, solenoid valve 11; 41, regulating valve Throttle valve 1; 42. Control valve 2; 43. Expansion control valve; 44. Oil control valve; 501. Flow meter 1; 502. Flow meter 2; 511. Temperature and pressure acquisition module 1; 512. Temperature and pressure acquisition module 2; 513. Temperature and pressure acquisition module 3; 514. Temperature and pressure acquisition module 4; 515. Temperature and pressure acquisition module 5; 516. Temperature acquisition module; 61. Oil separator; 62. Oil cooler; 63. Oil heater. DETAILED DESCRIPTION

[0050] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0051] Example 1

[0052] See also Figures 1 to 4 This embodiment provides a durability and performance coupling test device for a refrigeration compressor under accelerated conditions, including a refrigerant circulation component, a solenoid valve component, a controller and a data acquisition component, and may also include a regulating valve component and an oil circulation component.

[0053] The refrigerant circulation assembly includes a condenser 21, a liquid accumulator 22, a subcooler 23, and a calorimeter 24 connected in sequence. The inlet of the condenser 21 is connected to the exhaust end of the test compressor 1, and the outlet of the calorimeter 24 is connected to the suction end of the test compressor 1, forming a first refrigerant circulation loop for performance testing. The refrigerant circulation assembly also includes a mixing heat exchanger 25. The inlet of the mixing heat exchanger 25 is connected to the air supply pipeline before the inlet of the condenser 21 through an air inlet branch, and to the liquid supply pipeline after the outlet of the subcooler 23 through a liquid inlet branch. The outlet of the mixing heat exchanger 25 is connected to the suction end of the test compressor 1, forming a second refrigerant circulation loop for durability testing.

[0054] The solenoid valve assembly includes a plurality of solenoid valves arranged on the pipeline, namely, solenoid valve 1 31 to solenoid valve 11 311 .

[0055] The controller is used to adjust the pipeline connectivity by controlling multiple solenoid valves, thereby realizing the state switching between the performance test and the endurance test. During the performance test, the refrigerant discharged from the test compressor 1 is sequentially heat-exchanged through the condenser 21, the liquid accumulator 22, the subcooler 23, and the calorimeter 24 before returning to the test compressor 1. During the endurance test, part of the refrigerant discharged from the test compressor 1 enters the mixing heat exchanger 25 through the air inlet branch, and the other part enters the mixing heat exchanger 25 through the liquid inlet branch after passing through the condenser 21, the liquid accumulator 22, and the subcooler 23. The two refrigerants exchange heat in the mixing heat exchanger 25 before returning to the test compressor 1.

[0056] The regulating valve assembly includes a regulating valve 41 , a second regulating valve 42 , an expansion regulating valve 43 , and an oil regulating valve 44 .

[0057] The data acquisition component is used to collect refrigerant flow, temperature, and pressure data in multiple sections of piping during performance and durability testing. Specifically, the data acquisition component includes flow meter 1 501, flow meter 2 502, temperature and pressure acquisition module 1 511, temperature and pressure acquisition module 2 512, temperature and pressure acquisition module 3 513, temperature and pressure acquisition module 4 514, and temperature and pressure acquisition module 5 515. It may also include a temperature acquisition module 516.

[0058] It should be noted that the temperature and pressure acquisition module refers to a module that integrates temperature and pressure acquisition functions and can be composed of a temperature sensor and a pressure sensor installed in the same location. Temperature acquisition module 516, on the other hand, consists solely of a temperature sensor. Both flowmeter 1 501 and flowmeter 2 502 can be volumetric flowmeters.

[0059] The electromagnetic valve 1 31 is arranged on the pipeline between the exhaust end of the tested compressor 1 and the condenser 21, and the temperature and pressure acquisition module 1 511 is arranged on the pipeline between the exhaust end of the tested compressor 1 and the electromagnetic valve 1 31; the electromagnetic valve 2 32, the flow meter 1 501 and the expansion regulating valve 43 are arranged in sequence on the pipeline between the outlet of the subcooler 23 and the inlet of the calorimeter 24, and the temperature and pressure acquisition module 2 512 is arranged on the pipeline between the flow meter 1 501 and the expansion regulating valve 43; the electromagnetic valve 33 and the flow meter 2 502 are arranged in sequence on the pipeline between the outlet of the calorimeter 24 and the suction end of the tested compressor 1, and the temperature and pressure acquisition module 2 512 is arranged on the pipeline between the flow meter 1 501 and the expansion regulating valve 43. The collecting module three 513 is arranged on the pipeline between the outlet of the calorimeter 24 and the solenoid valve three 33, and the temperature and pressure collection module four 514 is arranged on the pipeline between the flow meter two 502 and the suction end of the test compressor 1; the solenoid valve four 34 and the regulating valve 41 are arranged on the intake branch in sequence, and the solenoid valve five 35 and the regulating valve two 42 are arranged on the liquid inlet branch in sequence; the outlet of the mixing heat exchanger 25 is connected to the pipeline between the flow meter two 502 and the temperature and pressure collection module four 514 through the solenoid valve six 36, and the temperature and pressure collection module five 515 is arranged on the pipeline between the outlet of the mixing heat exchanger 25 and the solenoid valve six 36.

[0060] The oil circulation assembly includes an oil separator 61, an oil cooler 62 and an oil heater 63; the refrigerant inlet and refrigerant outlet of the oil separator 61 are connected in parallel to the pipelines at both ends of the solenoid valve 1 31 through the solenoid valve 7 37 and the solenoid valve 8 38 respectively; the oil outlet of the oil separator 61 is divided into two oil outlet paths, of which the first oil outlet path is connected to the suction end of the test compressor 1 through the solenoid valve 9 39, the oil cooler 62, the oil heater 63, the oil regulating valve 44 and the temperature acquisition module 516 in sequence, and the first oil outlet path is used to regulate the temperature and flow of the recovered oil, and the second oil outlet path is directly connected to the suction end of the test compressor 1 through the solenoid valve 10 310.

[0061] The controller implements the following control strategy during the performance test:

[0062] Open solenoid valve seven 37, solenoid valve eight 38 and solenoid valve nine 39, and close solenoid valve one 31 and solenoid valve ten 310, so that the refrigerant discharged from the test compressor 1 passes through the oil separator 61 and the oil is recovered to the test compressor 1 through the first oil outlet; open solenoid valve two 32 and solenoid valve three 33, and close solenoid valve four 34, solenoid valve five 35 and solenoid valve six 36 to form a first refrigerant circulation loop and perform simulated load heat exchange on the refrigerant output from the subcooler 23 through the calorimeter 24.

[0063] During this performance test, the refrigerant discharged from the test compressor 1 enters the oil separator 61 through the solenoid valve 7 37 , where the oil is separated. The refrigerant then flows through the solenoid valve 8 38 into the condenser 21 , where it is condensed into a high-pressure liquid. It then flows into the liquid reservoir 22 , and then into the subcooler 23 , where its subcooling is further adjusted. After exiting, it passes through the solenoid valve 2 32 and enters the flow meter 1 501 . After throttling through the expansion regulating valve 43 , it enters the calorimeter 24 . It then flows through the solenoid valve 3 33 and the flow meter 2 502 , and enters the intake port of the test compressor 1 , completing one cycle. During the performance test, ensure that the hybrid heat exchanger 25 and its air and liquid inlet branches are not involved in the performance test process, and that the temperature and pressure acquisition modules 1 511 , 2 512 , 3 513 , 4 514 , and 516 are all in operation. This allows the calculation of the compressor's cooling capacity to be measured during the performance test. The oil separated by oil separator 61 passes through solenoid valve 939, oil cooler 62, oil heater 63, and oil regulating valve 44, ultimately returning to the intake port of test compressor 1. There, it joins the refrigerant entering the compressor, completing the cycle. Because the flow rate and temperature of the refrigeration oil need to be adjusted during performance testing, the solenoid valve 10310 in the oil circuit is closed.

[0064] During the durability test, the controller determines whether the durability test requires the intervention of the oil separator 61 and executes the following control strategy:

[0065] When no intervention is required: solenoid valve 1 31 is opened, and solenoid valves 7 37, 8 38, 9 39, and 10 310 are closed, allowing the refrigerant discharged from the test compressor 1 to bypass the oil separator 61. Solenoid valves 4 34, 5 35, and 6 36 are opened, and solenoid valves 2 32 and 3 33 are closed, forming a second refrigerant circulation loop. The oil-containing refrigerants from the air inlet branch and the liquid inlet branch are mixed and heat exchanged through the mixing heat exchanger 25. At this time, the refrigerant discharged from the test compressor 1 is divided into two paths after passing through solenoid valve 1 31. One path enters the condenser 21 and is condensed into a high-pressure liquid. It then flows into the liquid reservoir 22 and subcooler 23, where the subcooling degree is further adjusted. It then flows through solenoid valve 5 35 and regulating valve 2 42 before entering the mixing heat exchanger 25. The other path, high-temperature, high-pressure gas, passes through electric valve 4 34 and regulating valve 1 41 and enters the mixing heat exchanger 25. After mixing, the two refrigerants enter the mixing heat exchanger 25 for sufficient heat exchange to form low-pressure superheated refrigerant gas, which then flows through the solenoid valve 6 36 and enters the suction port of the tested compressor 1 to complete a cycle.

[0066] Some real operating systems also contain an oil separator 61. When the oil separator 61 needs to intervene: open solenoid valve 1 31 and solenoid valve 10 310, and close solenoid valve 7 37, solenoid valve 8 38 and solenoid valve 9 39, so that the refrigerant discharged from the test compressor 1 passes through the oil separator 61 and recovers the oil to the test compressor 1 through the second oil outlet; open solenoid valve 4 34, solenoid valve 5 35 and solenoid valve 6 36, and close solenoid valve 2 32 and solenoid valve 3 33 to form a second refrigerant circulation loop and mix the refrigerants from the air inlet branch and the liquid inlet branch through the mixing heat exchanger 25 for heat exchange.

[0067] One end of the solenoid valve 11 311 is connected to the pipeline between the temperature and pressure acquisition module 5 515 and the solenoid valve 6 36 , and the other end is connected to the enthalpy increase interface 101 of the tested compressor 1 with the air replenishment and enthalpy increase function.

[0068] In particular, for some tested compressors 1 with the air-injection and enthalpy-increasing function, the controller performs the following control strategy during the performance test (i.e., the heat pump operating performance test):

[0069] Open solenoid valve seven 37, solenoid valve eight 38 and solenoid valve nine 39, and close solenoid valve one 31 and solenoid valve ten 310, so that the refrigerant discharged from the test compressor 1 passes through the oil separator 61 and recovers the oil to the test compressor 1 through the first oil outlet; open solenoid valve two 32, solenoid valve three 33, solenoid valve four 34, solenoid valve five 35 and solenoid valve eleven 311, and close solenoid valve six 36, so that on the basis of forming the first refrigerant circulation loop, the air inlet branch and the liquid inlet branch are kept open, so that the mixing heat exchanger 25 delivers refrigerant to the enthalpy increase interface 101, forming an air replenishment and enthalpy increase circulation loop.

[0070] Among them, when performing a performance test on the test compressor 1 with the air replenishment and enthalpy increase function, among all the refrigerants returning to the suction port of the test compressor 1, the refrigerant output by the calorimeter 24 accounts for 75%-90%, and the refrigerant output by the mixing heat exchanger 25 accounts for 10%-25%.

[0071] During the heat pump operating performance test, the temperature and pressure acquisition modules 1 511 to 515 and the temperature acquisition module 516 are all put into use, and the measurement values ​​of the flow meter 1 501 and the flow meter 502 are combined to jointly calculate the compressor heat amount to be measured in the heat pump operating performance test.

[0072] See also Figure 5 This embodiment also provides a method for coupling endurance and performance testing of a refrigeration compressor under accelerated conditions, which is applied to the test device described above; the coupling test method comprises the following steps:

[0073] Step 1: Obtain the operating parameters of the test compressor 1 under the set actual operating conditions and the accelerated conditions of the endurance test respectively; the operating parameters include the compressor suction and exhaust temperature, suction and exhaust pressure, and suction specific volume.

[0074] Step 2: Calculate the acceleration factor σ between the actual operating condition and the accelerated condition based on the operating parameters under different operating conditions:

[0075] σ=(ΔP1 / ΔP0) a (v1 / v0) b ·exp(c(P 1D / P 0D )(1 / T0-1 / T1))

[0076] Wherein, ΔP1 is the ratio of the exhaust pressure to the suction pressure of the test compressor 1 under the acceleration condition, ΔP0 is the ratio of the exhaust pressure to the suction pressure of the test compressor 1 under the actual operating condition, and the unit is kPa / kPa; v1 is the suction specific volume of the test compressor 1 under the acceleration condition, and v0 is the suction specific volume of the test compressor 1 under the actual operating condition, and the unit is kg / m 3 ; T1 is the exhaust temperature of the test compressor 1 under accelerated conditions, T0 is the exhaust temperature of the test compressor 1 under actual operating conditions, the unit is Kelvin; P 1D and P 0D are the exhaust pressures of the tested compressor (1) under actual operating conditions and accelerated conditions, respectively; a, b and c are the pressure conversion coefficient, specific volume conversion coefficient and comprehensive conversion coefficient of the accelerated fatigue test, respectively; exp(·) is the natural exponential function.

[0077] Step 3: Obtain the designed service life of the test compressor 1 and divide it by the acceleration factor σ to obtain the durability test time of the test compressor 1. It should be noted that the designed service life refers to the designed or expected trouble-free operation time.

[0078] Step 4. Divide the durability test into multiple stages according to the duration of the durability test. Before the start of the durability test in each stage, conduct a performance test first. Then, adjust the pipeline connectivity status through the controller to conduct the durability test without stopping the machine, so as to conduct tests in all stages in turn and record the performance-related data and durability-related data during the test.

[0079] The performance-related data include the cooling capacity, energy efficiency ratio, circulating refrigerant flow, suction and exhaust temperature, suction and exhaust pressure and motor temperature of the test compressor 1; the durability-related data include the suction and exhaust temperature, suction and exhaust pressure, compressor power and ambient temperature of the test compressor 1.

[0080] Example 2

[0081] This embodiment uses the durability and performance coupling test device and method of the refrigeration compressor under accelerated conditions in Example 1 to test a certain model of train air-conditioning compressor.

[0082] For example, if a train air conditioning compressor runs 18 hours per day from May to October and 4 hours per day in April, and each month is 30 days, the total operating time of the compressor is calculated as follows: 6 × 30 × 18 + 30 × 4 = 3360 hours / year / unit. This compressor needs to operate reliably for three years, which means a mean trouble-free operating time of 10,080 hours.

[0083] Extensive testing using the device of the present invention has shown that applying accelerated model testing to the compressor under investigation allows for the development of a reliability-accelerated lifespan and real-time performance test model, thereby calculating the acceleration factor between actual operating conditions and accelerated operating conditions. The test model parameters include temperature, compressor suction / discharge pressure ratio, and compressor speed, and a composite model is created by combining the Arrhenius model and the inverse power law model.

[0084] In this embodiment, the calculation formula of the acceleration factor is:

[0085] σ=(ΔP1 / ΔP0) 3.6 (v1 / v0) 1.3 ·exp(6.97(P 1D / P 0D )(1 / T0-1 / T1))

[0086] The operating parameters of the compressor of this embodiment under a basic operating condition and an accelerated operating condition are shown in Table 1.

[0087] Table 1: Compressor operating parameters

[0088]

[0089] From the data in this table, we can calculate that the acceleration factor σ is 5.3. Therefore, the device and method of the present invention can be used for an endurance test for a time period of: 10080 / 5.3 = 1902 hours. A prototype was selected for an accelerated life performance test. The specific operating procedures are as follows:

[0090] a) The total duration of the endurance test of the compressor is T = 1902h. The endurance test process is divided into 3 stages, and the compressor runs continuously for 634h in each stage.

[0091] b) Carry out performance test first and switch the test device to performance mode.

[0092] c) Carry out the first stage of durability test for t=634h, and record the compressor operation data during the entire period of t, including the compressor suction and discharge temperature, suction and discharge pressure, ambient temperature, compressor power, etc.

[0093] d) After the endurance test (time t), the unit does not need to be shut down for piping replacement. Simply switch valves in the unit and conduct the same performance test as in step b) above. Compare the performance test results with those from the first step b), including cooling capacity, energy efficiency ratio, flow rate, suction and discharge pressure and temperature, and motor temperature.

[0094] e) Carry out the second stage of durability test for t=634h, and record the compressor operation data during the entire period of t: including the compressor suction and discharge temperature, suction and discharge pressure, ambient temperature, compressor power, etc.

[0095] f) After the endurance test (time t), the unit does not need to be shut down for piping replacement. Simply switch valves in the unit and conduct the same performance test as in step b) above. Compare the performance test results from the first and second b) stages, including cooling capacity, energy efficiency ratio, flow rate, suction and discharge pressure and temperature, and motor temperature.

[0096] g) Conduct the third stage t=634h durability test and record the compressor operation data during the entire period t: including compressor suction and discharge temperature, suction and discharge pressure, ambient temperature, compressor power, etc.

[0097] The above description is only a preferred specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any technician familiar with the technical field, within the technical scope disclosed by the present invention, who makes equivalent replacements or changes based on the technical solution and inventive concept of the present invention, should be covered by the scope of protection of the present invention.

Claims

1. A refrigeration compressor durability and performance coupling test device under accelerated conditions, characterized in that: include: A refrigerant circulation assembly comprises a condenser (21), a liquid accumulator (22), a subcooler (23) and a calorimeter (24) connected in sequence, wherein the inlet of the condenser (21) is connected to the exhaust end of the test compressor (1), and the outlet of the calorimeter (24) is connected to the suction end of the test compressor (1), forming a first refrigerant circulation loop for performance testing; the refrigerant circulation assembly further comprises a mixing heat exchanger (25), wherein the inlet of the mixing heat exchanger (25) is connected to the gas transmission pipeline before the inlet of the condenser (21) through an air inlet branch, and is connected to the liquid transmission pipeline after the outlet of the subcooler (23) through a liquid inlet branch, and the outlet of the mixing heat exchanger (25) is connected to the suction end of the test compressor (1), forming a second refrigerant circulation loop for durability testing; A solenoid valve assembly includes a plurality of solenoid valves arranged on a pipeline; The controller is used to adjust the pipeline connection state by controlling multiple solenoid valves, thereby realizing the state switching between the performance test and the endurance test; wherein, during the performance test, the refrigerant discharged from the test compressor (1) is sequentially heat-exchanged through the condenser (21), the liquid accumulator (22), the subcooler (23), and the calorimeter (24) and then returned to the test compressor (1); during the endurance test, part of the refrigerant discharged from the test compressor (1) enters the mixing heat exchanger (25) through the air inlet branch, and the other part enters the mixing heat exchanger (25) through the liquid inlet branch after passing through the condenser (21), the liquid accumulator (22), and the subcooler (23); the two refrigerants exchange heat in the mixing heat exchanger (25) and then return to the test compressor (1); The data acquisition component is used to collect the flow, temperature and pressure data of the refrigerant in multiple sections of pipelines during performance and durability tests.

2. The durability and performance coupling test device for refrigeration compressors under accelerated conditions according to claim 1, characterized in that: Also includes: A regulating valve assembly, comprising a regulating valve (41), a second regulating valve (42) and an expansion regulating valve (43); The solenoid valve assembly includes a solenoid valve 1 (31), a solenoid valve 2 (32), a solenoid valve 3 (33), a solenoid valve 4 (34), a solenoid valve 5 (35), and a solenoid valve 6 (36); The data acquisition component includes flow meter 1 (501), flow meter 2 (502), temperature and pressure acquisition module 1 (511), temperature and pressure acquisition module 2 (512), temperature and pressure acquisition module 3 (513), temperature and pressure acquisition module 4 (514) and temperature and pressure acquisition module 5 (515); Wherein, the solenoid valve 1 (31) is arranged on the pipeline between the exhaust end of the tested compressor (1) and the condenser (21), and the temperature and pressure acquisition module 1 (511) is arranged on the pipeline between the exhaust end of the tested compressor (1) and the solenoid valve 1 (31); the solenoid valve 2 (32), the flow meter 1 (501) and the expansion regulating valve (43) are arranged in sequence on the pipeline between the outlet of the subcooler (23) and the inlet of the calorimeter (24), and the temperature and pressure acquisition module 2 (512) is arranged on the pipeline between the flow meter 1 (501) and the expansion regulating valve (43); the solenoid valve 3 (33) and the flow meter 2 (502) are arranged in sequence on the pipeline between the outlet of the calorimeter (24) and the suction end of the tested compressor (1), and the temperature and pressure acquisition module 2 (512) is arranged on the pipeline between the flow meter 1 (501) and the expansion regulating valve (43). The pressure acquisition module three (513) is arranged on the pipeline between the outlet of the calorimeter (24) and the electromagnetic valve three (33), and the temperature and pressure acquisition module four (514) is arranged on the pipeline between the flow meter two (502) and the suction end of the test compressor (1); the electromagnetic valve four (34) and the regulating valve (41) are arranged on the air inlet branch in sequence, and the electromagnetic valve five (35) and the regulating valve two (42) are arranged on the liquid inlet branch in sequence; the outlet of the mixing heat exchanger (25) is connected to the pipeline between the flow meter two (502) and the temperature and pressure acquisition module four (514) through the electromagnetic valve six (36), and the temperature and pressure acquisition module five (515) is arranged on the pipeline between the outlet of the mixing heat exchanger (25) and the electromagnetic valve six (36).

3. The durability and performance coupling test device for refrigeration compressors under accelerated conditions according to claim 2, characterized in that: The regulating valve assembly further includes an oil regulating valve (44); The solenoid valve assembly further includes a solenoid valve seven (37), a solenoid valve eight (38), a solenoid valve nine (39) and a solenoid valve ten (310); The data acquisition component further includes a temperature acquisition module (516); The test device also includes: An oil circulation assembly comprises an oil separator (61), an oil cooler (62) and an oil heater (63); a refrigerant inlet and a refrigerant outlet of the oil separator (61) are connected in parallel to pipelines at both ends of the solenoid valve (31) through a solenoid valve (7) (37) and a solenoid valve (8) (38) respectively; an oil outlet of the oil separator (61) is divided into two oil outlet paths, wherein the first oil outlet path is connected to the suction end of the tested compressor (1) through a solenoid valve (9) (39), an oil cooler (62), an oil heater (63), an oil regulating valve (44) and a temperature acquisition module (516) in sequence, and the first oil outlet path is used to control the temperature and flow of the recovered oil, and the second oil outlet path is directly connected to the suction end of the tested compressor (1) through a solenoid valve (10) (310).

4. The durability and performance coupling test device for refrigeration compressors under accelerated conditions according to claim 3, characterized in that: The controller implements the following control strategy during the performance test: Open solenoid valve seven (37), solenoid valve eight (38) and solenoid valve nine (39), and close solenoid valve one (31) and solenoid valve ten (310), so that the refrigerant discharged from the test compressor (1) passes through the oil separator (61) and the oil is recovered to the test compressor (1) through the first oil outlet; open solenoid valve two (32) and solenoid valve three (33), and close solenoid valve four (34), solenoid valve five (35) and solenoid valve six (36), so as to form a first refrigerant circulation loop and perform simulated load heat exchange on the refrigerant output from the subcooler (23) through the calorimeter (24).

5. The durability and performance coupling test device for refrigeration compressors under accelerated conditions according to claim 3, characterized in that: During the durability test, the controller determines whether the durability test requires the intervention of the oil separator (61) and executes the following control strategy: When intervention is required: open solenoid valve 1 (31) and solenoid valve 10 (310), and close solenoid valve 7 (37), solenoid valve 8 (38) and solenoid valve 9 (39), so that the refrigerant discharged from the test compressor (1) passes through the oil separator (61) and the oil is recovered to the test compressor (1) through the second oil outlet; open solenoid valve 4 (34), solenoid valve 5 (35) and solenoid valve 6 (36), and close solenoid valve 2 (32) and solenoid valve 3 (33), so as to form a second refrigerant circulation loop and mix the refrigerants from the air inlet branch and the liquid inlet branch through the mixing heat exchanger (25); When intervention is not required: open solenoid valve one (31), and close solenoid valve seven (37), solenoid valve eight (38), solenoid valve nine (39) and solenoid valve ten (310), so that the refrigerant discharged from the test compressor (1) bypasses the oil separator (61); open solenoid valve four (34), solenoid valve five (35) and solenoid valve six (36), and close solenoid valve two (32) and solenoid valve three (33), so as to form a second refrigerant circulation loop and mix the oil-containing refrigerant from the air inlet branch and the liquid inlet branch through the mixing heat exchanger (25).

6. The durability and performance coupling test device for refrigeration compressors under accelerated conditions according to claim 3, characterized in that: The solenoid valve assembly further includes a solenoid valve eleven (311); one end of the solenoid valve eleven (311) is connected to the pipeline between the temperature and pressure acquisition module five (515) and the solenoid valve six (36), and the other end is connected to the enthalpy increase interface (101) of the tested compressor (1) having the air supply and enthalpy increase function.

7. The durability and performance coupling test device for refrigeration compressors under accelerated conditions according to claim 6, characterized in that: For the tested compressor (1) with the air-injection and enthalpy-increasing function, the controller executes the following control strategy during the performance test: Open solenoid valve seven (37), solenoid valve eight (38) and solenoid valve nine (39), and close solenoid valve one (31) and solenoid valve ten (310), so that the refrigerant discharged from the test compressor (1) passes through the oil separator (61) and the oil is recovered to the test compressor (1) through the first oil outlet; open solenoid valve two (32), solenoid valve three (33), solenoid valve four (34), solenoid valve five (35) and solenoid valve eleven (311), and close solenoid valve six (36), so that on the basis of forming a first refrigerant circulation loop, the air inlet branch and the liquid inlet branch are kept open, so that the mixing heat exchanger (25) delivers refrigerant to the enthalpy increase interface (101), forming an air supply and enthalpy increase circulation loop.

8. The device for coupling durability and performance testing of refrigeration compressors under accelerated conditions according to claim 7, characterized in that: When a performance test is conducted on a test compressor (1) having an air supply and enthalpy increase function, among all the refrigerants returning to the suction port of the test compressor (1), the refrigerant output by the calorimeter (24) accounts for 75%-90%, and the refrigerant output by the mixing heat exchanger (25) accounts for 10%-25%.

9. A method for coupling durability and performance testing of refrigeration compressors under accelerated conditions, characterized in that: Applicable to the test device according to any one of claims 3 to 8; the coupling test method comprises the following steps: Step 1: respectively obtaining the operating parameters of the test compressor (1) under the set actual operating conditions and the accelerated operating conditions of the endurance test; the operating parameters include the compressor suction and exhaust temperature, suction and exhaust pressure, and suction specific volume; Step 2: Calculate the acceleration factor σ between the actual operating condition and the accelerated condition based on the operating parameters under different operating conditions: σ=(ΔP1 / ΔP0) a ·(v1 / v0) b ·exp(c(P 1D / P 0D (1 / T0-1 / T1)) Wherein, ΔP1 is the ratio of the exhaust pressure to the suction pressure of the test compressor (1) under the acceleration condition, ΔP0 is the ratio of the exhaust pressure to the suction pressure of the test compressor (1) under the actual operating condition, and the unit is kPa / kPa; v1 is the suction specific volume of the test compressor (1) under the acceleration condition, and v0 is the suction specific volume of the test compressor (1) under the actual operating condition, and the unit is kg / m 3 ; T1 is the exhaust temperature of the test compressor (1) under accelerated working conditions, T0 is the exhaust temperature of the test compressor (1) under actual operating conditions, the unit is Kelvin; P 1D and P 0D are the exhaust pressures of the tested compressor (1) under actual operating conditions and accelerated conditions, respectively; a, b, and c are the pressure conversion coefficient, specific volume conversion coefficient, and comprehensive conversion coefficient of the accelerated fatigue test, respectively; exp(·) is the natural exponential function; Step 3: Obtain the designed service life of the test compressor (1) and divide it by the acceleration factor σ to obtain the durability test life of the test compressor (1); Step 4. Divide the durability test into multiple stages according to the duration of the durability test. Before the start of the durability test in each stage, conduct a performance test first. Then, adjust the pipeline connectivity status through the controller to conduct the durability test without stopping the machine, so as to conduct tests in all stages in turn and record the performance-related data and durability-related data during the test.

10. The device for coupling endurance and performance testing of refrigeration compressors under accelerated conditions according to claim 9, characterized in that: The performance-related data include the cooling capacity, energy efficiency ratio, circulating refrigerant flow, suction and exhaust temperature, suction and exhaust pressure, and motor temperature of the tested compressor (1); and the durability-related data include the suction and exhaust temperature, suction and exhaust pressure, compressor power, and ambient temperature of the tested compressor (1).

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