Method for testing performance of compressor of non-azeotropic mixed working medium

Abstract

This invention provides a performance testing method for a non-azeotropic refrigerant compressor, relating to the field of compressor testing technology. The method accurately verifies the cooling capacity and coefficient of performance (COP) of a non-azeotropic refrigerant compressor at a specific operating point. When the verification is accurate, the cooling capacity and COP at that operating point are used as the standard cooling capacity and standard COP for the compressor at that point. This allows for testing of non-azeotropic refrigerant compressors with different refrigerant types and component ratios to obtain standard cooling capacity and standard COP. Subsequent mass production of the compressor uses these standard cooling capacity and standard COP as the benchmark for performance quality inspection, standardizing the performance inspection process and ensuring the stability of the non-azeotropic refrigerant compressor product performance. It also facilitates accurate selection of non-azeotropic refrigerant compressors by manufacturers of refrigeration equipment such as refrigerators.

Description

Technical Field

[0001] This invention relates to the field of compressor testing technology, and more specifically to a method for testing the performance of a compressor with a non-azeotropic working fluid. Background Technology

[0002] To test compressor performance (standard cooling capacity and standard coefficient of performance), the operating point of the compressor must first be determined. For pure refrigerant compressors, the operating point is determined by the saturation temperature. However, for non-azeotropic refrigerant compressors, the temperature changes continuously during evaporation and condensation, exhibiting a glide temperature. The existence of the glide temperature means that the evaporation and condensation temperatures cannot be determined as simply as for pure refrigerant compressors. Furthermore, different types and component ratios of non-azeotropic refrigerants result in variations in the performance (standard cooling capacity and standard coefficient of performance) of their compressors. Currently, there is no unified industry method for testing the performance of non-azeotropic refrigerant compressors, posing significant challenges. This also complicates compressor selection for refrigeration equipment such as refrigerators. Replacing the compressor in the later stages of product development can extend the project development cycle, while replacing the compressor after the product has been launched will lead to large-scale recalls and repairs. Summary of the Invention

[0003] The purpose of this invention is to provide a method for testing the performance of a non-azeotropic refrigerant compressor, so as to accurately determine the standard refrigeration capacity and standard coefficient of performance of the non-azeotropic refrigerant compressor.

[0004] To achieve the above objectives, the technical solution adopted by the present invention is as follows:

[0005] A method for testing the performance of a compressor containing a non-azeotropic working fluid, the method comprising the following steps:

[0006] Step 1: Select the operating point of the compressor for a non-azeotropic mixture.

[0007] Based on the pressure-enthalpy diagram of the non-azeotropic working fluid, the non-azeotropic working fluid compressor selects several operating points, each of which includes the discharge pressure corresponding to the condensation temperature and the suction pressure corresponding to the evaporation temperature.

[0008] Step 2: Operational test of the non-azeotropic mixture compressor

[0009] The cooling capacity and coefficient of performance of the non-azeotropic refrigerant compressor were tested at various operating points.

[0010] Step 3: Matching Test

[0011] Each operating point corresponds to a pure refrigerant compressor. The cooling capacity and coefficient of performance of the pure refrigerant compressor at the standard operating point are the same as those of the non-azeotropic mixed refrigerant compressor at the set operating point. The non-azeotropic mixed refrigerant compressor and each pure refrigerant compressor are connected to the same refrigeration equipment to test the cooling rate and power consumption.

[0012] Step 4: Determine the standard refrigeration capacity and standard coefficient of performance of the non-azeotropic refrigerant compressor.

[0013] If the cooling rate of the non-azeotropic mixture compressor is the same as the cooling rate of the pure compressor at any operating point, then the cooling capacity at that operating point is the standard cooling capacity of the non-azeotropic mixture compressor at that operating point.

[0014] If the power consumption of a non-azeotropic mixture compressor is the same as that of a pure compressor at any operating point, then the performance coefficient of that operating point is the standard performance coefficient of the non-azeotropic mixture compressor at that operating point.

[0015] Preferably, in step 1, the non-azeotropic working fluid compressor selects at least three operating points, with operating point 1 including the condensation dew point temperature T. kg The corresponding pressure P kg The exhaust pressure is T, and the evaporation dew point temperature is T. zg The corresponding pressure P zg The suction pressure is given, and operating point 2 includes the condensation point temperature T. kq The corresponding pressure P kq The exhaust pressure is T, and the evaporation point temperature is T. zq The corresponding pressure P zq The suction pressure is given, and operating point 3 includes the condensation point temperature T. kq The corresponding pressure P kq With condensation dew point temperature T kg The corresponding pressure P kg The arithmetic mean is the exhaust pressure and the evaporation point temperature T. zq The corresponding pressure P zq With evaporation dew point temperature T zg The corresponding pressure P zg The arithmetic mean is the inhalation pressure.

[0016] Preferably, the non-azeotropic working fluid in the compressor includes R600a and R290, with a mass ratio of R600a to R290 of 6:4; the pure working fluid in the compressor is R290.

[0017] Preferably, in step 2, the cooling capacity and coefficient of performance of the non-azeotropic mixture compressor at each operating point are tested based on the second refrigerant thermostat method.

[0018] Preferably, the refrigeration device in step 3 is a refrigerator.

[0019] The beneficial technical effects of this invention are:

[0020] The performance testing method for non-azeotropic refrigerant compressors of the present invention can accurately verify the cooling capacity of a non-azeotropic refrigerant compressor at a certain operating point, and when the verification is accurate, the cooling capacity at that operating point is taken as the standard cooling capacity of the non-azeotropic refrigerant compressor at that operating point; it can also accurately verify the coefficient of performance (COP) of a non-azeotropic refrigerant compressor at a certain operating point, and when the verification is accurate, the COP is taken as the standard COP of the non-azeotropic refrigerant compressor at that operating point; thus, standard cooling capacity and standard COP can be obtained by testing non-azeotropic refrigerant compressors with different types of mixed refrigerants and different component ratios. During subsequent mass production of compressors, the standard cooling capacity and standard COP are used as the standard for performance quality inspection, standardizing performance quality inspection and stabilizing the performance of non-azeotropic refrigerant compressor products. This also facilitates manufacturers of refrigerators and other refrigeration equipment to accurately select non-azeotropic refrigerant compressors. Attached Figure Description

[0021] Figure 1 This is a flowchart of a performance testing method for a non-azeotropic mixed working fluid compressor according to an embodiment of the present invention;

[0022] Figure 2 This is a pressure-enthalpy diagram of a non-azeotropic working fluid according to an embodiment of the present invention;

[0023] Figure 3 This is a schematic diagram of the experimental principle of the second refrigeration dose heater method in an embodiment of the present invention. Detailed Implementation

[0024] To make the objectives, technical solutions, and beneficial effects of this invention clearer, the invention will be further described in detail below with reference to specific embodiments and the accompanying drawings. Certain embodiments of the invention will be described more fully below with reference to the accompanying drawings, and some, but not all, of these embodiments will be shown. In fact, various embodiments of the invention can be implemented in many different forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided to enable the invention to meet applicable legal requirements.

[0025] In the description of this invention, it should be noted that the terms "inner," "outer," "upper," "lower," "front," and "rear," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and for simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0026] In this embodiment of the invention, a method for testing the performance of a non-azeotropic working fluid compressor is provided. Please refer to [reference needed]. Figures 1 to 3 As shown.

[0027] A method for testing the performance of a compressor containing a non-azeotropic mixture includes the following steps:

[0028] Step 1: Select the operating point of the compressor for a non-azeotropic mixture.

[0029] like Figure 2 As shown, based on the pressure-enthalpy diagram of the non-azeotropic working fluid, three operating points are selected for the non-azeotropic working fluid compressor. Each operating point includes the discharge pressure corresponding to the condensation temperature and the suction pressure corresponding to the evaporation temperature. Specifically, operating point 1 includes the condensation dew point temperature T... kg The corresponding pressure P kg The exhaust pressure is T, and the evaporation dew point temperature is T. zg The corresponding pressure P zg The suction pressure is given, and operating point 2 includes the condensation point temperature T. kq The corresponding pressure P kq The exhaust pressure is T, and the evaporation point temperature is T. zq The corresponding pressure P zq The suction pressure is given, and operating point 3 includes the condensation point temperature T. kq The corresponding pressure P kq With condensation dew point temperature T kg The corresponding pressure P kg The arithmetic mean is the exhaust pressure and the evaporation point temperature T. zq The corresponding pressure P zq With evaporation dew point temperature T zg The corresponding pressure P zg The arithmetic mean is the inhalation pressure.

[0030] Step 2: Operational test of the non-azeotropic mixture compressor

[0031] Based on the second refrigerant thermostat method, the cooling capacity and coefficient of performance of a non-azeotropic mixture compressor at various operating points were tested.

[0032] GB / T 9098-2021, "Fully Enclosed Electric Motors - Compressors for Refrigerators," stipulates that refrigerator compressors should be tested using the second refrigerant calorimeter method according to Clause 5.1 of GB / T5773-2016, "Performance Test Methods for Positive Displacement Refrigeration Compressors." The second refrigerant calorimeter method is based on the principle of thermal balance. Inside the calorimeter, a second refrigerant is used as the medium. The cooling and heating outputs of the compressor are balanced, keeping the second refrigerant at a constant temperature and pressure. By measuring the heating power meter, the compressor's cooling capacity and coefficient of performance can be measured. The schematic diagram of the test apparatus for the second refrigerant calorimeter method is shown below. Figure 3 As shown.

[0033] Step 3: Matching Test

[0034] Each operating point corresponds to a pure refrigerant compressor. The cooling capacity and coefficient of performance of the pure refrigerant compressor at the standard operating point are the same as those of the non-azeotropic mixed refrigerant compressor at the set operating point. The non-azeotropic mixed refrigerant compressor and each pure refrigerant compressor are connected to the same refrigeration equipment for cooling speed and power consumption tests.

[0035] Among them, the non-azeotropic working fluid in the non-azeotropic working fluid compressor includes R600a and R290, and the mass ratio of R600a and R290 is 6:4; the pure working fluid in the pure working fluid compressor is R290.

[0036] As shown in Table 1, step 2 includes the cooling capacity and coefficient of performance (COP) of a non-azeotropic refrigerant compressor (compressor A) at three operating points, and the cooling capacity and COP of pure refrigerant compressors (compressors B, C, and D) at the same three operating points. Specifically, the cooling capacity and COP of compressor B at the standard operating point are the same as those of compressor A at operating point 1; the cooling capacity and COP of compressor C at the standard operating point are the same as those of compressor A at operating point 2; and the cooling capacity and COP of compressor D at the standard operating point are the same as those of compressor A at operating point 3.

[0037] Table 1. Three operating points of the non-azeotropic mixed refrigerant compressor and the corresponding parameters of the pure refrigerant compressor.

[0038]

[0039] The test results of step 3 are shown in Table 2:

[0040] Table 2. Test results of refrigerator cooling speed and power consumption

[0041]

[0042] Step 4: Determine the standard refrigeration capacity and standard coefficient of performance of the non-azeotropic refrigerant compressor.

[0043] If the cooling rate of the non-azeotropic mixture compressor is the same as the cooling rate of the pure compressor at any operating point, then the cooling capacity at that operating point is the standard cooling capacity of the non-azeotropic mixture compressor at that operating point.

[0044] If the power consumption of a non-azeotropic mixture compressor is the same as that of a pure compressor at any operating point, then the performance coefficient of that operating point is the standard performance coefficient of the non-azeotropic mixture compressor at that operating point.

[0045] Referring to Table 2, in this embodiment, the cooling rate of compressor A is the same as that of compressor C. The operating point corresponding to compressor C is operating point 2, and the cooling capacity of operating point 2 is the standard cooling capacity of compressor A at operating point 2. The power consumption of compressor A is the same as that of compressor D. The operating point corresponding to compressor D is operating point 3, and the performance coefficient of operating point 3 is the standard performance coefficient of compressor A at operating point 3.

[0046] The present invention has been described in detail with reference to the accompanying drawings. Based on the above description, those skilled in the art should have a clear understanding of the performance testing method for non-azeotropic refrigerant compressors of the present invention. The performance testing method for non-azeotropic refrigerant compressors of the present invention can accurately verify the cooling capacity of a non-azeotropic refrigerant compressor at a certain operating point, and when the verification is accurate, use the cooling capacity at that operating point as the standard cooling capacity of the non-azeotropic refrigerant compressor at that operating point; it can also accurately verify the coefficient of performance (COP) of a non-azeotropic refrigerant compressor at a certain operating point, and when the verification is accurate, use the COP as the standard COP of the non-azeotropic refrigerant compressor at that operating point; thus, standard cooling capacity and standard COP can be obtained by testing non-azeotropic refrigerant compressors with different refrigerant types and component ratios. During subsequent mass production of compressors, the standard cooling capacity and standard COP are used as standards for performance quality inspection, standardizing performance quality inspection and stabilizing the performance of non-azeotropic refrigerant compressor products. This also facilitates accurate selection of non-azeotropic refrigerant compressors by manufacturers of refrigeration equipment such as refrigerators.

[0047] The specific embodiments described above further illustrate the purpose, technical solution, and beneficial effects of the present invention. It should be understood that the above descriptions are merely specific embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A method for testing the performance of a compressor containing a non-azeotropic working fluid, characterized in that, The method includes the following steps: Step 1: Select the operating point of the compressor for a non-azeotropic mixture. Based on the pressure-enthalpy diagram of the non-azeotropic working fluid, the non-azeotropic working fluid compressor selects several operating points, each of which includes the discharge pressure corresponding to the condensation temperature and the suction pressure corresponding to the evaporation temperature. In step 1, the non-azeotropic working fluid compressor selects at least three operating points, with operating point 1 including the condensation dew point temperature T. kg The corresponding pressure P kg The exhaust pressure is T, and the evaporation dew point temperature is T. zg The corresponding pressure P zg The suction pressure is given, and operating point 2 includes the condensation point temperature T. kq The corresponding pressure P kq The exhaust pressure is T, and the evaporation point temperature is T. zq The corresponding pressure P zq The suction pressure is given, and operating point 3 includes the condensation point temperature T. kq The corresponding pressure P kq With condensation dew point temperature T kg The corresponding pressure P kg The arithmetic mean is the exhaust pressure and the evaporation point temperature T. zq The corresponding pressure P zq With evaporation dew point temperature T zg The corresponding pressure P zg The arithmetic mean is the inhalation pressure; Step 2: Operational test of the non-azeotropic mixture compressor The cooling capacity and coefficient of performance of the non-azeotropic refrigerant compressor were tested at various operating points. Step 3: Matching Test Each operating point corresponds to a pure refrigerant compressor. The cooling capacity and coefficient of performance of the pure refrigerant compressor at the standard operating point are the same as those of the non-azeotropic refrigerant compressor at the set operating point. The non-azeotropic refrigerant compressor and each pure refrigerant compressor are connected to the same refrigeration equipment for cooling speed and power consumption testing. Step 4: Determine the standard refrigeration capacity and standard coefficient of performance of the non-azeotropic refrigerant compressor. If the cooling rate of the non-azeotropic mixture compressor is the same as the cooling rate of the pure compressor at any operating point, then the cooling capacity at that operating point is the standard cooling capacity of the non-azeotropic mixture compressor at that operating point. If the power consumption of a non-azeotropic mixture compressor is the same as that of a pure compressor at any operating point, then the performance coefficient of that operating point is the standard performance coefficient of the non-azeotropic mixture compressor at that operating point.

2. The method for testing the performance of a non-azeotropic working fluid compressor according to claim 1, characterized in that: In a non-azeotropic compressor, the non-azeotropic working fluid includes R600a and R290, with a mass ratio of R600a to R290 of 6:4; in a pure working fluid compressor, the pure working fluid is R290.

3. The method for testing the performance of a non-azeotropic working fluid compressor according to claim 1, characterized in that: In step 2, based on the second refrigerant thermostat method, the cooling capacity and coefficient of performance of the non-azeotropic mixture compressor at each operating point are tested.

4. The method for testing the performance of a non-azeotropic working fluid compressor according to claim 1, characterized in that: The refrigeration device in step 3 is set as a refrigerator.

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