Performance testing device for double-suction double-row compressor

Abstract

The application discloses a double-suction double-row compressor performance testing device, which comprises a first refrigerant circuit, a first oil return circuit, a second refrigerant circuit and a second oil return circuit. The parameters of the circuits are independently controlled through a condenser, a supercooler, an oil separator, a calorimeter and multiple adjusting valves, so that the accuracy and authenticity of the performance and durability test data of the double-suction double-row compressor are ensured.

Description

Technical Field

[0001] This invention specifically relates to a performance testing device for a double-suction, double-discharge compressor. Background Technology

[0002] Currently, most air conditioner indoor units use a double-row heat exchanger structure. When air flows through the first row of heat exchangers, the air temperature changes, causing the temperature difference with the second row to decrease, which may reduce heat exchange performance. Especially in dehumidification mode, electric auxiliary heating is required to control the ambient temperature within a suitable range, thereby reducing energy consumption. To address these issues, many compressor and air conditioner manufacturers have begun developing dual-suction, dual-row compressors, which control the evaporation and condensation temperatures separately, allowing for differentiated control of the evaporation and condensation temperatures of the double-row heat exchangers according to operating conditions.

[0003] The interface of the double-suction double-exhaust compressor is as follows Figure 1 As shown, this type of compressor has two exhaust ports and two intake ports. The system refrigerant enters from the intake port and exits from the exhaust port, forming the first refrigerant circuit. The system refrigerant enters from the intake port and exits from the exhaust port, forming the second refrigerant circuit. Under different operating conditions, the intake pressure, exhaust pressure, intake temperature, and inlet temperature of the two refrigerant circuits are different, and the refrigerant flow rate is also different, so that the two refrigerant circuits can achieve different cooling or heating capacities for different operating conditions.

[0004] Given the structural characteristics and application scenarios of dual-suction, dual-row compressors, testing their performance requires separate control of the intake and exhaust of the compressor's dual intake and dual exhaust ports. However, existing compressor performance and durability testing equipment is designed for single-suction, single-row compressors with one intake port and one exhaust port, and cannot be used for performance testing of dual-suction, dual-row compressors.

[0005] In addition, there are also such as Figure 2 The single-suction double-row compressor shown is and Figure 3 The illustrated dual-suction single-row compressor has one intake port (Port 1) and two exhaust ports (Port 1 and Port 2), forming a refrigerant circuit with one intake port and two exhaust ports. The exhaust pressures of the two exhaust ports are different. Under the same operating conditions, the intake pressure and temperature are the same, but the refrigerant flow rates of the two exhaust ports are different. The dual-suction single-row compressor has two intake ports (Port 1 and Port 2) and one exhaust port (Port 1), forming a refrigerant circuit. The intake pressure or temperature of the two intake ports may differ. Therefore, neither the single-suction double-row compressor nor the dual-suction single-row compressor can be subjected to performance and durability tests using existing testing equipment. Summary of the Invention

[0006] The purpose of this invention is to provide a performance testing device for a double-suction, double-row compressor, which aims to accurately test the performance and durability of the double-suction, double-row compressor.

[0007] The technical solution of the present invention is as follows:

[0008] A performance testing device for a dual-suction, dual-discharge compressor includes:

[0009] First refrigerant circuit: One end is connected to the compressor's exhaust port 1, and passes sequentially through regulating valve VG11, first oil separator, regulating valve VG12, first condenser, first subcooler, regulating valve VC11, first calorimeter, and regulating valve VG13 before being connected to the compressor's suction port 1 at the other end. A first refrigerant flow meter is installed between the first subcooler and the first calorimeter.

[0010] The return port of the first oil separator is connected to the first return oil circuit. After passing through the regulating valve VG14, regulating valve VG15, oil cooler, and regulating valve VG16 in sequence, the end of the first return oil circuit is connected between the first calorimeter and the regulating valve VG13 in the first refrigerant circuit. A first return oil flow meter is installed between the regulating valve VG14 and the regulating valve VG15.

[0011] The second refrigerant circuit is connected at one end to the second discharge port of the compressor, and then passes through the regulating valve VG21, the second oil separator, the regulating valve VG22, the second condenser, the second subcooler, the regulating valve VC21, the second calorimeter, and the regulating valve VG23 in sequence before being connected at the other end to the second suction port of the compressor. A second refrigerant flow meter is installed between the second subcooler and the second calorimeter.

[0012] The return port of the second oil separator is connected to the second return oil circuit. After passing through the regulating valve VG24, regulating valve VG25, oil cooler, and regulating valve VG26 in sequence, the end of the second return oil circuit is connected between the second calorimeter and regulating valve VG23 in the second refrigerant circuit. A second return oil flow meter is installed between regulating valve VG24 and regulating valve VG25.

[0013] The main parameters involved in the compressor performance test of this invention are as follows.

[0014] Intake pressure: The gas pressure at the compressor's intake port;

[0015] Discharge pressure: The gas pressure at the compressor's discharge port;

[0016] Valve inlet pressure: The pressure before the evaporator expansion valve of the compressor during the refrigeration cycle;

[0017] Suction temperature: The refrigerant temperature at the compressor suction port;

[0018] Discharge temperature: The refrigerant temperature at the compressor discharge port;

[0019] Valve inlet temperature: The temperature before the evaporator expansion valve of the compressor during the refrigeration cycle;

[0020] Refrigerant flow rate: The mass flow rate of refrigerant flowing in the refrigerant circuit;

[0021] Oil return flow rate: The flow rate of oil that returns to the compressor suction port after being processed by the oil separator via the oil return line.

[0022] This invention employs a second refrigerant heater method for compressor performance testing, wherein...

[0023] The first condenser and the second condenser control the exhaust pressure of the exhaust port one and exhaust port two of the double-suction double-row compressor, respectively.

[0024] The first subcooler and the second subcooler control the inlet temperature of the regulating valve VC11 in the first refrigerant circuit and the inlet temperature of the regulating valve VC21 in the second refrigerant circuit, respectively.

[0025] The first calorimeter and the second calorimeter control the suction temperature or enthalpy increase temperature before the suction port one and suction port two of the double suction double exhaust compressor by controlling their respective electric heating amounts.

[0026] When using the calorimeter method, regulating valves VC11 and VC21 control the suction pressure before suction port one and suction port two of the double-suction double-outlet compressor by their respective opening degrees.

[0027] The regulating valves VG15 and VG25 adjust the return oil flow of the first return oil circuit and the second return oil circuit respectively by their respective opening degrees;

[0028] The first refrigerant flow meter and the second refrigerant flow meter are high-precision mass flow meters used to test the refrigerant mass flow of the first refrigerant circuit and the second refrigerant circuit, respectively.

[0029] The first and second oil separators separate the refrigerant from the oil coming out of the first and second exhaust ports of the double-suction double-exhaust compressor, ensuring the authenticity and accuracy of the refrigerant mass flow test.

[0030] The first and second oil return flow meters respectively measured the actual oil return volume at suction port one and suction port two of the double-suction double-row compressor;

[0031] The oil cooler is used to regulate the return oil temperature of the first and second return oil circuits.

[0032] The testing device of this invention enables independent control of various parameters in the two refrigerant circuits of a double-suction, double-row compressor, allowing for performance testing using the second refrigerant calorimeter method. Furthermore, this invention can be coupled with a multi-way regulating valve to switch between the gas loop method and the calorimeter method, facilitating testing under non-steady-state conditions such as rapid start-stop and frequency sweep conditions. A preferred design is as follows:

[0033] In this invention, the two ends of the regulating valve VG12 of the first refrigerant circuit are connected through the first bypass I. The first bypass I is provided with a regulating valve VC12. The regulating valve VG12 of the first refrigerant circuit is connected to the first condenser through a first bypass J. The end of the first bypass J is connected between the regulating valve VC11 of the first refrigerant circuit and the first calorimeter. The first bypass J is provided with a regulating valve VC13.

[0034] The two ends of the regulating valve VG22 of the second refrigerant circuit are connected through the second bypass branch O. The second bypass branch O is equipped with a regulating valve VC22. The regulating valve VG22 of the second refrigerant circuit is connected to the second condenser through a second bypass branch P. The end of the second bypass branch P is connected between the regulating valve VC21 of the second refrigerant circuit and the second calorimeter. A regulating valve VC23 is installed on the second bypass branch P.

[0035] When using the calorimeter method, regulating valves VC12, VC13, VC22, and VC23 are all closed.

[0036] When using the air ring method, both regulating valves VG12 and VG22 are closed. The discharge pressure of the double-suction double-row compressor's discharge port one and discharge port two are controlled by adjusting the opening of regulating valves VC12 and VC22, respectively. The suction pressure of the double-suction double-row compressor's suction port one and suction port two are controlled by adjusting the opening of regulating valves VC13 and VC23, respectively. The suction temperature of the double-suction double-row compressor's suction port one and suction port two is controlled by adjusting the opening of regulating valves VC11 and VC21, respectively.

[0037] The present invention can also be further optimized with the following preferred designs for performance testing of dual-suction single-row compressors, single-suction dual-row compressors, dual-suction single-row compressors, and single-suction single-row compressors. Specific solutions are as follows:

[0038] In this invention, the first return oil circuit is provided with a regulating valve VG17 on the pipeline at the rear end of the regulating valve VG16, and the second return oil circuit is connected between the oil cooler and the regulating valve VG26 with a first intermediate branch provided with a regulating valve VG27. The end of the first intermediate branch is connected between the regulating valve VG16 and the regulating valve VG17 in the first return oil circuit.

[0039] In this invention, a regulating valve V3 is provided between the second refrigerant circuit and the second refrigerant flow meter, and a regulating valve V4 is provided between the second refrigerant flow meter and the second calorimeter. A second intermediate branch with a regulating valve V1 is connected between the second refrigerant flow meter and the regulating valve V4. The end of the second intermediate branch is connected between the first refrigerant circuit and the first refrigerant flow meter.

[0040] In this invention, a third intermediate branch with a regulating valve V2 is connected between the first subcooler and the first refrigerant flow meter in the first refrigerant circuit. The end of the third intermediate branch is connected between the second subcooler and the second refrigerant flow meter in the second refrigerant circuit.

[0041] In this invention, the first condenser, the first subcooler, the second condenser, the second subcooler, and the oil cooler are all connected to the chiller unit via their respective adjustable water circulation pipelines. The flow rate of circulating water into the first condenser, the first subcooler, the second condenser, the second subcooler, and the oil cooler is controlled by valves with adjustable opening, thereby adjusting each parameter.

[0042] The first refrigerant circuit of the present invention is provided with a temperature sensor T11 and a pressure sensor P11 at the connection end with the compressor's exhaust port to obtain the exhaust temperature and exhaust pressure of the exhaust port. The first refrigerant circuit is provided with a temperature sensor T12 and a pressure sensor P12 at the connection end with the compressor's suction port to obtain the suction temperature and suction pressure of the suction port. A temperature sensor T13 and a pressure sensor P13 are provided between the first refrigerant flow meter of the first refrigerant circuit and the regulating valve VC11 to obtain the inlet temperature and inlet pressure of the first refrigerant circuit.

[0043] A temperature sensor T21 and a pressure sensor P21 are installed at the connection end between the second refrigerant circuit and the second discharge port of the compressor to obtain the discharge temperature and discharge pressure of the second discharge port. A temperature sensor T22 and a pressure sensor P22 are installed at the connection end between the second refrigerant circuit and the second suction port of the compressor to obtain the suction temperature and suction pressure of the second suction port. A temperature sensor T23 and a pressure sensor P23 are installed between the second refrigerant flow meter of the second refrigerant circuit and the regulating valve VC21 to obtain the inlet temperature and inlet pressure of the second refrigerant circuit.

[0044] The first refrigerant circuit of the present invention is provided with a temperature sensor T14 and a pressure sensor P14 at the outlet end of the first calorimeter to accurately obtain the temperature and pressure at the outlet of the first calorimeter, so as to accurately calculate the enthalpy change between the inlet end and the outlet end of the first calorimeter.

[0045] The second refrigerant circuit is equipped with a temperature sensor T24 and a pressure sensor P24 at the outlet of the second calorimeter to accurately obtain the temperature and pressure at the outlet of the second calorimeter, which is used to accurately calculate the enthalpy change between the inlet and outlet of the second calorimeter.

[0046] In the first return oil circuit of the present invention, a temperature sensor T15 is provided between the oil cooler and the regulating valve VG16 to obtain the return oil temperature of the first return oil circuit.

[0047] A temperature sensor T25 is installed between the oil cooler and the regulating valve VG26 in the second return oil circuit to obtain the return oil temperature of the second return oil circuit.

[0048] The first bypass branch J of the present invention is provided with a temperature sensor T16 and a pressure sensor P16 at the rear end of the regulating valve VC13 to obtain the temperature and pressure of the first bypass branch J, and to provide a basis for adjusting the opening degree of the regulating valve VC13 in the air ring method.

[0049] The second bypass branch P is equipped with a temperature sensor T26 and a pressure sensor P26 at the rear end of the regulating valve VC23 to obtain the temperature and pressure of the second bypass branch P, providing a basis for adjusting the opening of the regulating valve VC23 in the air ring method.

[0050] The beneficial effects of this invention are as follows:

[0051] 1. The testing device of the present invention, for a dual-suction dual-row compressor, constructs two refrigerant circuits, which can independently control various parameters on the refrigerant circuits, ensuring the accuracy of the performance and durability test data of the dual-suction dual-row compressor.

[0052] 2. This invention, when combined with a multi-way regulating valve, enables the conversion between the gas loop method and the calorimeter method for testing. The gas loop method is used to test non-steady-state conditions such as rapid start-stop and frequency sweep conditions of the compressor.

[0053] 3. By setting multiple regulating valves, this invention can also realize the performance testing of double-suction single-row compressors, single-suction double-row compressors, double-suction single-row compressors, and single-suction single-row compressors, thus improving the versatility of the testing device. Attached Figure Description

[0054] Figure 1 This is a schematic diagram of a double-suction, double-row compressor;

[0055] Figure 2 This is a schematic diagram of a single-suction, double-row compressor;

[0056] Figure 3 This is a schematic diagram of a double-suction single-row compression surface;

[0057] Figure 4 This is a schematic diagram of the working principle of the performance testing device for a double-suction, double-discharge compressor of the present invention.

[0058] Figure 5 This is a schematic diagram of the condenser and subcooler of the present invention;

[0059] Figure 6 This invention and Figure 5 A schematic diagram of a chiller unit with a central condenser and subcooler connected;

[0060] Figure 7This is a schematic diagram illustrating the working principle of a double-suction, double-discharge compressor for performance testing.

[0061] Figure 8 This is a schematic diagram illustrating the working principle of a single-suction, double-row compressor for performance testing.

[0062] Figure 9 This is a schematic diagram illustrating the working principle of a double-suction single-row compressor for performance testing.

[0063] Figure 10 This is a schematic diagram illustrating the working principle of a single-suction, single-row compressor for performance testing. Detailed Implementation

[0064] The technical solution of the present invention will be described in detail below with reference to the accompanying drawings and embodiments, so that those skilled in the art can better understand and implement the technical solution of the present invention.

[0065] like Figures 4 to 10 As shown, a performance testing device for a dual-suction, dual-row compressor includes:

[0066] First refrigerant circuit: One end is connected to the compressor's exhaust port 1, and passes sequentially through regulating valve VG11, first oil separator 14, regulating valve VG12, first condenser 11, first subcooler 12, regulating valve VC11, first calorimeter 13, and regulating valve VG13 before being connected to the compressor's suction port 1 at the other end. A first refrigerant flow meter 15 is installed between the first subcooler 12 and the first calorimeter 13.

[0067] The return port of the first oil separator 14 is connected to the first return oil circuit. After passing through the regulating valve VG14, regulating valve VG15, oil cooler 3, and regulating valve VG16 in sequence, the end of the first return oil circuit is connected between the first calorimeter 13 and the regulating valve VG13 in the first refrigerant circuit. A first return oil flow meter 16 is installed between the regulating valve VG14 and the regulating valve VG15.

[0068] The second refrigerant circuit is connected to the second discharge port of the compressor at one end, and then passes through the regulating valve VG21, the second oil separator 24, the regulating valve VG22, the second condenser 21, the second subcooler 22, the regulating valve VC21, the second calorimeter 23, and the regulating valve VG23 in sequence, before being connected to the second suction port of the compressor at the other end. A second refrigerant flow meter 25 is installed between the second subcooler 22 and the second calorimeter 23.

[0069] The return port of the second oil separator 24 is connected to the second return oil circuit. After passing through the regulating valve VG24, regulating valve VG25, oil cooler 3, and regulating valve VG26 in sequence, the end of the second return oil circuit is connected between the second calorimeter 23 and the regulating valve VG23 in the second refrigerant circuit. A second return oil flow meter 26 is installed between the regulating valve VG24 and the regulating valve VG25.

[0070] The compressor performance was tested using the second refrigerant thermostat method, in which...

[0071] The first condenser 11 and the second condenser 21 respectively control the exhaust pressure of the exhaust port one and exhaust port two of the double suction double row compressor A;

[0072] The first subcooler 12 and the second subcooler 22 respectively control the inlet temperature before the regulating valve VC11 in the first refrigerant circuit and the inlet temperature before the regulating valve VC21 in the second refrigerant circuit;

[0073] The first calorimeter 13 and the second calorimeter 23 control the suction temperature or enthalpy increase temperature before the suction port 1 and suction port 2 of the double suction double row compressor A by controlling their respective electric heating amounts.

[0074] When using the calorimeter method, regulating valves VC11 and VC21 control the suction pressure before suction port 1 and suction port 2 of the double-suction double-row compressor A by their respective opening degrees.

[0075] The regulating valves VG15 and VG25 adjust the return oil flow of the first return oil circuit and the second return oil circuit respectively by their respective opening degrees;

[0076] The first refrigerant flow meter 15 and the second refrigerant flow meter 25 use high-precision mass flow meters to test the refrigerant mass flow of the first refrigerant circuit and the second refrigerant circuit, respectively.

[0077] The first oil separator 14 and the second oil separator 24 separate the refrigerant and oil coming out of the exhaust port 1 and exhaust port 2 of the double-suction double-row compressor A, ensuring the authenticity and accuracy of the refrigerant mass flow test.

[0078] The first oil return flow meter 16 and the second oil return flow meter 26 respectively test the actual oil return volume at the suction port 1 and suction port 2 of the double suction double row compressor A.

[0079] Oil cooler 3 is used to regulate the return oil temperature of the first and second return oil circuits.

[0080] This example enables the conversion between the gas loop method and the calorimeter method for testing, allowing for testing of non-steady-state conditions such as rapid start-stop and frequency sweep conditions of the compressor. A preferred embodiment is as follows:

[0081] The regulating valve VG12 of the first refrigerant circuit is connected at both ends through the first bypass I. The first bypass I is equipped with a regulating valve VC12. The regulating valve VG12 of the first refrigerant circuit is connected to the first condenser 11 through a first bypass J. The end of the first bypass J is connected between the regulating valve VC11 of the first refrigerant circuit and the first calorimeter 13. The first bypass J is equipped with a regulating valve VC13.

[0082] The two ends of the regulating valve VG22 of the second refrigerant circuit are connected through the second bypass branch O. The second bypass branch O is equipped with a regulating valve VC22. The regulating valve VG22 of the second refrigerant circuit is connected to the second condenser through a second bypass branch P. The end of the second bypass branch P is connected between the regulating valve VC21 of the second refrigerant circuit and the second calorimeter 23. The second bypass branch P is equipped with a regulating valve VC23.

[0083] When using the calorimeter method, regulating valves VC12, VC13, VC22, and VC23 are all closed.

[0084] When using the air ring method, both regulating valves VG12 and VG22 are closed. The discharge pressure of the double-suction double-row compressor A at discharge port 1 and discharge port 2 is controlled by adjusting the opening of regulating valves VC12 and VC22, respectively. The suction pressure of the double-suction double-row compressor A at suction port 1 and suction port 2 is controlled by adjusting the opening of regulating valves VC13 and VC23, respectively. The suction temperature of the double-suction double-row compressor A at suction port 1 and suction port 2 is controlled by adjusting the opening of regulating valves VC11 and VC21, respectively.

[0085] This embodiment, through the following preferred design, can be used for performance testing of dual-suction single-row compressors, single-suction dual-row compressors, dual-suction single-row compressors, and single-suction single-row compressors. Specifically:

[0086] The first return oil circuit has a regulating valve VG17 installed on the pipeline at the rear end of the regulating valve VG16. The second return oil circuit has a first intermediate branch with a regulating valve VG27 connected between the oil cooler 3 and the regulating valve VG26. The end of the first intermediate branch is connected between the regulating valve VG16 and the regulating valve VG17 in the first return oil circuit.

[0087] The second refrigerant circuit is provided with a regulating valve V3 between the second subcooler 22 and the second refrigerant flow meter 25, and a regulating valve V4 between the second refrigerant flow meter 25 and the second calorimeter 23. A second intermediate branch with a regulating valve V1 is connected between the second refrigerant flow meter and the regulating valve V4. The end of the second intermediate branch is connected between the first subcooler 12 and the first refrigerant flow meter 15 of the first refrigerant circuit.

[0088] A third intermediate branch with a regulating valve V2 is connected between the first subcooler 12 and the first refrigerant flow meter 15 in the first refrigerant circuit. The end of the third intermediate branch is connected between the second subcooler 22 and the second refrigerant flow meter 25 in the second refrigerant circuit.

[0089] The first condenser 11, first subcooler 12, second condenser 21, second subcooler 22, and oil cooler 3 are all connected to the chiller unit 5 via their respective adjustable water circulation pipelines. The flow rate and temperature of the circulating water entering the first condenser 11, first subcooler 12, second condenser 21, second subcooler 22, and oil cooler 3 are controlled by valves with adjustable opening. The controlled water flow exchanges heat with the refrigerant or return oil to adjust these parameters. For details, please refer to [link to relevant documentation]. Figure 5 and Figure 6 The first condenser 11 is connected to the chiller unit 5 via connectors 1OUT and 1IN, the first subcooler 12 is connected to the chiller unit 5 via connectors 2OUT and 2IN, the second condenser 21 is connected to the chiller unit 5 via connectors 3OUT and 3IN, and the second subcooler 22 is connected to the chiller unit 5 via connectors 4OUT and 4IN. Regulating valves WVCTW-D, WVSRW-D, WVCTW-X, and WVSRW-X are respectively installed on the connecting pipes to regulate the water flow rate of each circulating water pipe. Thermostats HEAC-D, HEAS-D, HEAC-X, and HEAS-X are also respectively installed on the connecting pipes to work with the chiller unit 5 to regulate the water temperature of each circulating water pipe.

[0090] A temperature sensor T11 and a pressure sensor P11 are installed at the connection end between the first refrigerant circuit and the compressor's discharge port to obtain the discharge temperature and discharge pressure of the discharge port. A temperature sensor T12 and a pressure sensor P12 are installed at the connection end between the first refrigerant circuit and the compressor's suction port to obtain the suction temperature and suction pressure of the suction port. A temperature sensor T13 and a pressure sensor P13 are installed between the first refrigerant flow meter of the first refrigerant circuit and the regulating valve VC11 to obtain the inlet temperature and inlet pressure of the first refrigerant circuit.

[0091] A temperature sensor T21 and a pressure sensor P21 are installed at the connection end between the second refrigerant circuit and the second discharge port of the compressor to obtain the discharge temperature and discharge pressure of the second discharge port. A temperature sensor T22 and a pressure sensor P22 are installed at the connection end between the second refrigerant circuit and the second suction port of the compressor to obtain the suction temperature and suction pressure of the second suction port. A temperature sensor T23 and a pressure sensor P23 are installed between the second refrigerant flow meter of the second refrigerant circuit and the regulating valve VC21 to obtain the inlet temperature and inlet pressure of the second refrigerant circuit.

[0092] The first refrigerant circuit is equipped with a temperature sensor T14 and a pressure sensor P14 at the outlet end of the first calorimeter 13 to accurately obtain the temperature and pressure at the outlet of the first calorimeter 13, and to accurately calculate the enthalpy change between the inlet and outlet ends of the first calorimeter 13.

[0093] The second refrigerant circuit is equipped with a temperature sensor T24 and a pressure sensor P24 at the outlet end of the second calorimeter 23 to accurately obtain the temperature and pressure at the outlet of the second calorimeter 23, and to accurately calculate the enthalpy change between the inlet and outlet ends of the second calorimeter 23.

[0094] A temperature sensor T15 is installed between the oil cooler 3 and the regulating valve VG16 in the first return oil circuit to obtain the return oil temperature of the first return oil circuit.

[0095] A temperature sensor T25 is installed between the oil cooler 3 and the regulating valve VG26 in the second return oil circuit to obtain the return oil temperature of the second return oil circuit.

[0096] The first bypass branch J is equipped with a temperature sensor T16 and a pressure sensor P16 at the rear end of the regulating valve VC13 to obtain the temperature and pressure of the first bypass branch J, providing a basis for adjusting the opening of the regulating valve VC13 in the air ring method.

[0097] The second bypass branch P is equipped with a temperature sensor T26 and a pressure sensor P26 at the rear end of the regulating valve VC23 to obtain the temperature and pressure of the second bypass branch P, providing a basis for adjusting the opening of the regulating valve VC23 in the air ring method.

[0098] Example 1: Performance and durability testing of a double-suction, double-row compressor using the second refrigerant thermostat method.

[0099] refer to Figure 4 The test device for obtaining a double-suction, double-discharge compressor A after closing regulating valves V1 and V2 is as follows: Figure 7As shown, regulating valves VC12, VC13, VC22, VC23, and VG27 are all closed. The first refrigerant circuit and the first oil return circuit are formed between the first exhaust port and the first suction port of the double-suction double-row compressor A, while the second refrigerant circuit and the second oil return circuit are formed between the second exhaust port and the second suction port. In the first refrigerant circuit, the exhaust pressure at exhaust port one is controlled by the first condenser 11, the suction pressure at suction port one is controlled by the opening of regulating valve VC11, the suction temperature at suction port one is controlled by the first calorimeter 13, the inlet temperature of regulating valve VC11 is controlled by the first subcooler 12, the return oil temperature in the first return oil circuit is controlled by the oil cooler 3, and the return oil flow rate at the first return oil flow meter 16 is controlled by the opening of regulating valve VG15. In the second refrigerant circuit, the exhaust pressure at exhaust port two is controlled by the second condenser 21, the suction pressure at suction port two is controlled by the opening of regulating valve VC21, the suction temperature at suction port two is controlled by the second calorimeter 23, and the regulating valve VG15... The temperature before valve C21 is controlled by the second subcooler 22, the return oil temperature of the second return oil circuit is controlled by the oil cooler 3, and the return oil volume at the second return oil meter 26 is controlled by the opening of the regulating valve VG25. By independently controlling the above parameters, the refrigerant flow rate and enthalpy changes in the first and second refrigerant circuits can be obtained under different operating conditions using the second refrigerant superheater method. Accurate results of the compressor's cooling capacity, heating capacity, power, volumetric efficiency, and other performance can be obtained. The device can also be used to perform durability tests on the double-suction double-row compressor A under specified conditions. If compressor noise needs to be tested, the compressor should be placed in the anechoic chamber 4 during the test.

[0100] Experimental Example 2: Unsteady-state test of a double-suction, double-row compressor using the gas ring method.

[0101] Based on Experiment 1, control valves VG12 and VG22 are closed, while control valves VC12, VC13, VC22, and VC23 are opened. The internal heating of the first calorimeter 13 and the second calorimeter 23 is shut off. The difference from Experiment 1 is that, in this case, the exhaust pressure at exhaust port one in the first refrigerant circuit is controlled by the opening of control valve VC12, the suction pressure at suction port one is controlled by the opening of control valve VC13, and the suction temperature at suction port one is controlled by the opening of control valve VC11. Similarly, in the second refrigerant circuit, the exhaust pressure at exhaust port two is controlled by the opening of control valve VC22, the suction pressure at suction port two is controlled by the opening of control valve VC23, and the suction temperature at suction port two is controlled by the opening of control valve VC21. The gas loop method can be used to test the performance of the double-suction double-row compressor under non-steady-state conditions such as rapid start-stop and frequency sweep conditions.

[0102] Test Example 3: Performance and durability testing of a single-suction double-row compressor using the second refrigerant thermostat method.

[0103] refer to Figure 4 After closing regulating valves V2, VC12, VC13, VC21, VC22, VC23, V4, and VG26, a test device for a single-suction double-row compressor B is obtained, as follows: Figure 8 As shown, the first refrigerant circuit and the first oil return circuit are the same as in Test Example 1. The refrigerant from exhaust port 2 passes through regulating valve VG21, the second oil separator 24, regulating valve VG22, the second condenser 21, the second subcooler 22, regulating valve V3, and the second refrigerant flow meter 25, then passes through regulating valve V1 of the second intermediate branch to reach the first refrigerant flow meter 15 in the first refrigerant circuit, and finally returns to intake port 1. The oil return from the second oil separator 24 passes through regulating valve VG24, the second oil return flow meter 26, regulating valve VG25, oil cooler 3, and regulating valve VG27 of the first intermediate branch before entering the first oil return circuit, and finally returns to intake port 1. The adjustment principle of each parameter in Test Example 3 is the same as that in Test Example 1, and will not be described in detail here. It can be used for the performance and durability testing of single-suction double-row compressor B.

[0104] Experiment Example 4: Performance and durability testing of a double-suction single-row compressor using the second refrigerant thermostat method.

[0105] refer to Figure 4 After closing regulating valves V1, V3, VG27, VC12, and VC13, a test device for a double-suction single-row compressor C is obtained, as follows: Figure 9 As shown, its first return oil circuit is the same as that in Test Example 1. The difference is that in Test Example 1, the first subcooler 12 and the first refrigerant flow meter 15 of the first refrigerant circuit are connected to a third intermediate branch, so that part of the refrigerant from exhaust port one returns to the suction port two of the double-suction single-row compressor C through the regulating valve V2, the second refrigerant flow meter 25, the regulating valve VC21, the regulating valve V4, the second calorimeter 23, and the regulating valve VG23 of the third intermediate branch. The control principle of each parameter is the same as that in Test Example 1, which can be used to perform performance and durability tests on the double-suction single-row compressor C.

[0106] Example 5: Unsteady-state test of a double-suction single-row compressor using the gas ring method.

[0107] like Figure 9As shown, based on Experiment 4, the regulating valve VG12 is closed, the internal heating of the first calorimeter 13 is turned off, and the regulating valves VC12 and VC13 are opened. The suction pressure of suction port one is controlled by the opening of regulating valve VC13, the suction temperature of suction port one is controlled by regulating valve VC11, the suction pressure of suction port two is controlled by the opening of regulating valve VC21, and the suction temperature of suction port two is controlled by the second calorimeter 23. The control principle of the remaining parameters is the same as that of Experiment 2. The gas ring method can be used to test the performance of the double-suction single-row compressor under non-steady-state conditions such as rapid start-stop and frequency sweep conditions.

[0108] Example 6: Performance and durability testing of a single-suction, single-row compressor using the second refrigerant thermostat method.

[0109] In this experimental example, the single-suction, single-row compressor D has only one intake port and one exhaust port. The following is achieved by controlling the opening and closing of each regulating valve: Figure 10 The test device for the single-suction, single-row compressor D shown has the regulating valves VC12 and VC13 closed. The difference from test example 1 is that only the first refrigerant circuit and the first oil return circuit are formed between the exhaust port 1 and the suction port 1. Its working principle is the same as that of test example 1.

[0110] Example 7: Unsteady-state test of a single-row, single-suction compressor using the gas ring method.

[0111] like Figure 10 As shown, when regulating valve VG12 is closed and regulating valves VC12 and VC13 are opened, only the same first refrigerant circuit and first return oil circuit as in test example 2 are formed, and its working principle is the same as that in test example 2.

[0112] This invention can perform performance and durability tests on double-suction double-row compressors, single-suction double-row compressors, double-suction single-row compressors, and single-suction single-row compressors. It can also switch between the calorimeter method and the gas ring method to achieve testing under non-steady-state operating conditions of the compressor.

[0113] The above embodiments are merely preferred embodiments of the present invention, but should not be construed as limiting the invention. Any modifications and improvements made based on the concept of the present invention should fall within the protection scope of the present invention, and the specific protection scope is subject to the claims.

Claims

1. A performance testing device for a double-suction, double-row compressor, characterized in that, include: First refrigerant circuit: One end is connected to the compressor's exhaust port 1, and passes sequentially through regulating valve VG11, first oil separator, regulating valve VG12, first condenser, first subcooler, regulating valve VC11, first calorimeter, and regulating valve VG13 before being connected to the compressor's suction port 1 at the other end. A first refrigerant flow meter is installed between the first subcooler and the first calorimeter. The return port of the first oil separator is connected to the first return oil circuit. After passing through the regulating valve VG14, regulating valve VG15, oil cooler, and regulating valve VG16 in sequence, the end of the first return oil circuit is connected between the first calorimeter and the regulating valve VG13 in the first refrigerant circuit. A first return oil flow meter is installed between the regulating valve VG14 and the regulating valve VG15. The second refrigerant circuit is connected at one end to the second discharge port of the compressor, and then passes through the regulating valve VG21, the second oil separator, the regulating valve VG22, the second condenser, the second subcooler, the regulating valve VC21, the second calorimeter, and the regulating valve VG23 in sequence before being connected at the other end to the second suction port of the compressor. A second refrigerant flow meter is installed between the second subcooler and the second calorimeter. The return port of the second oil separator is connected to the second return oil circuit. After passing through the regulating valve VG24, regulating valve VG25, oil cooler, and regulating valve VG26 in sequence, the end of the second return oil circuit is connected between the second calorimeter and the regulating valve VG23 in the second refrigerant circuit. A second return oil flow meter is installed between the regulating valve VG24 and the regulating valve VG25. The regulating valve VG12 of the first refrigerant circuit is connected to both ends through the first bypass I. The first bypass I is equipped with a regulating valve VC12. The regulating valve VG12 of the first refrigerant circuit is connected to the first condenser through a first bypass J. The end of the first bypass J is connected between the regulating valve VC11 of the first refrigerant circuit and the first calorimeter. The first bypass J is equipped with a regulating valve VC13. The first bypass J is equipped with a temperature sensor T16 and a pressure sensor P16 at the rear end of the regulating valve VC13. The two ends of the regulating valve VG22 of the second refrigerant circuit are connected through the second bypass branch O. The second bypass branch O is equipped with a regulating valve VC22. The regulating valve VG22 of the second refrigerant circuit is connected to the second condenser through a second bypass branch P. The end of the second bypass branch P is connected between the regulating valve VC21 of the second refrigerant circuit and the second calorimeter. A regulating valve VC23 is installed on the second bypass branch P. A temperature sensor T26 and a pressure sensor P26 are installed at the rear end of the regulating valve VC23 on the second bypass branch P.

2. The performance testing device for a double-suction, double-row compressor according to claim 1, characterized in that: The first return oil circuit has a regulating valve VG17 installed on the pipeline at the rear end of the regulating valve VG16. The second return oil circuit has a first intermediate branch with a regulating valve VG27 connected between the oil cooler and the regulating valve VG26. The end of the first intermediate branch is connected between the regulating valve VG16 and the regulating valve VG17 in the first return oil circuit.

3. The performance testing device for a double-suction, double-row compressor according to claim 2, characterized in that: The second refrigerant circuit is provided with a regulating valve V3 between the second subcooler and the second refrigerant flow meter, and a regulating valve V4 between the second refrigerant flow meter and the second calorimeter. A second intermediate branch with a regulating valve V1 is connected between the second refrigerant flow meter and the regulating valve V4. The end of the second intermediate branch is connected between the first subcooler and the first refrigerant flow meter of the first refrigerant circuit.

4. The performance testing device for a double-suction, double-row compressor according to claim 3, characterized in that: A third intermediate branch with a regulating valve V2 is connected between the first subcooler of the first refrigerant circuit and the first refrigerant flow meter. The end of the third intermediate branch is connected between the second subcooler of the second refrigerant circuit and the second refrigerant flow meter.

5. The performance testing device for a double-suction, double-row compressor according to any one of claims 1 to 4, characterized in that: The first condenser, the first subcooler, the second condenser, the second subcooler, and the oil cooler are all connected to the chiller unit through their respective adjustable water circulation pipelines.

6. The performance testing device for a double-suction, double-row compressor according to claim 5, characterized in that: A temperature sensor T11 and a pressure sensor P11 are installed at one connection end between the first refrigerant circuit and the compressor's exhaust port; a temperature sensor T12 and a pressure sensor P12 are installed at one connection end between the first refrigerant circuit and the compressor's suction port; and a temperature sensor T13 and a pressure sensor P13 are installed between the first refrigerant flow meter of the first refrigerant circuit and the regulating valve VC11. Temperature sensor T21 and pressure sensor P21 are installed at the second refrigerant circuit connection end with the compressor's exhaust port 2. Temperature sensor T22 and pressure sensor P22 are installed at the second refrigerant circuit connection end with the compressor's intake port 2. Temperature sensor T23 and pressure sensor P23 are installed between the second refrigerant flow meter of the second refrigerant circuit and the regulating valve VC21.

7. The performance testing device for a double-suction, double-row compressor according to claim 6, characterized in that: The first refrigerant circuit is equipped with a temperature sensor T14 and a pressure sensor P14 at the outlet end of the first calorimeter. The second refrigerant circuit is equipped with a temperature sensor T24 and a pressure sensor P24 at the outlet of the second calorimeter.

8. The performance testing device for a double-suction, double-row compressor according to claim 7, characterized in that: A temperature sensor T15 is installed between the oil cooler and the regulating valve VG16 in the first oil return circuit; The second return oil circuit has a temperature sensor T25 installed between the oil cooler and the regulating valve VG26.

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