Compressor performance testing apparatus and methods

Abstract

This invention relates to the field of compressor performance testing, and provides a compressor performance testing apparatus and method. The compressor performance testing apparatus includes a compressor under test, a condenser, a throttling device, and an evaporator. The discharge port of the compressor under test, the condenser, the throttling device, the evaporator, and the suction port of the compressor under test are sequentially connected via pipelines to form a refrigerant circulation loop. It also includes a regenerator, which has a high-temperature side channel and a low-temperature side channel. The high-temperature side channel is connected in series between the discharge port of the compressor under test and the inlet of the condenser, and the low-temperature side channel is connected in series between the outlet of the throttling device and the inlet of the evaporator. This compressor performance testing apparatus, with the same auxiliary temperature control system configuration, can test compressors with higher power and a wider cooling capacity range, thus broadening the applicability of the testing apparatus.

Description

Technical Field

[0001] This invention relates to the field of compressor performance testing, and provides a compressor performance testing device and method. Background Technology

[0002] The statements herein are provided only as background information in connection with this application and do not necessarily constitute prior art.

[0003] In refrigeration, air conditioning, and heat pump systems, the compressor is one of the core components, and its performance testing is crucial for product development, quality control, and energy efficiency assessment. Traditional compressor performance testing methods typically employ calorimetry or refrigerant flow meter methods. The refrigerant liquid flow meter method involves a testing system including the compressor under test, condenser, subcooler, flow meter, throttling device (such as an expansion valve), and evaporator. The basic principle of this method is that the high-temperature, high-pressure gaseous refrigerant discharged from the compressor releases heat in the condenser, condensing into a high-pressure liquid. It then passes through a throttling device to reduce its pressure, becoming a low-temperature, low-pressure gas-liquid two-phase fluid. Finally, it absorbs heat and evaporates in the evaporator, returning to the compressor to complete the cycle. The cooling capacity can be obtained by calculating the difference between the enthalpy after throttling and the compressor's suction enthalpy, multiplied by the flow rate.

[0004] To precisely control the operating conditions of the condenser and evaporator, traditional testing equipment requires independent, large-capacity constant-temperature liquid refrigeration units or electric heating devices. The condenser needs a cooling medium (such as an aqueous ethylene glycol solution) at a specific temperature to maintain the condensation temperature, while the evaporator needs a heating medium at a specific temperature to maintain the evaporation temperature. This auxiliary temperature control equipment consumes a significant amount of electrical energy, increasing both the initial investment cost and operating expenses. Therefore, traditional testing equipment is energy-intensive, especially when testing high-power or high-pressure-ratio compressors, which places extremely high demands on the condenser's heat exchange capacity and the cooling system's capacity. Furthermore, because the testing range using calorimetry or testing systems (such as refrigerant flow meter methods) typically does not exceed 20 times the refrigeration capacity, the equipment's ability to measure the compressor's refrigeration capacity range is limited. Summary of the Invention

[0005] This invention provides a compressor performance testing device to address the shortcomings of related technologies, such as high energy consumption, limited testing range, and heavy reliance on auxiliary temperature control equipment in compressor performance testing.

[0006] This invention also provides a method for testing compressor performance.

[0007] A first aspect of the present invention provides a compressor performance testing device, comprising a compressor under test, a condenser, a throttling device, and an evaporator. The discharge port of the compressor under test, the condenser, the throttling device, the evaporator, and the suction port of the compressor under test are sequentially connected via pipelines to form a refrigerant circulation loop. The device also includes a regenerator, which has a high-temperature side channel and a low-temperature side channel. The high-temperature side channel is connected in series between the discharge port of the compressor under test and the inlet of the condenser, and the low-temperature side channel is connected in series between the outlet of the throttling device and the inlet of the evaporator.

[0008] According to one embodiment of the present invention, the device further includes a subcooler and a flow meter, the subcooler being disposed between the outlet of the condenser and the inlet of the throttling element, and the flow meter being used to measure the refrigerant flow rate through the subcooler; The subcooler has a refrigerant passage and a cooling medium passage; the compressor performance testing device also includes a sensor for measuring the parameters of the cooling medium flowing through the cooling medium passage, in order to calculate the refrigerant flow rate and calibrate it with the reading of the flow meter.

[0009] According to one embodiment of the present invention, it further includes an installation passage for connecting to the plate heat exchanger under test, the installation passage being disposed at the refrigerant side and cooling water side inlet and outlet of the condenser for connecting the external plate heat exchanger; The installation path includes a temperature sensor for measuring the temperature of the refrigerant as it enters and exits the condenser. The temperature sensor is located at the inlet and outlet of the cooling water channel of the condenser. The temperature sensor is also used to measure the inlet and outlet temperatures of the cooling water to calculate the heat exchange and heat transfer coefficient.

[0010] According to one embodiment of the present invention, it further includes: The first bypass pipeline is connected in parallel with the high-temperature side channel of the regenerator; The second bypass pipeline is connected in parallel with the low-temperature side channel of the regenerator; A valve assembly for controlling the selective flow of refrigerant through the regenerator or through the first bypass line and the second bypass line.

[0011] According to one embodiment of the present invention, the valve assembly includes a proportional three-way valve, the inlet of which is connected to the outlet of the throttling element, the first outlet of which is connected to the low-temperature side passage of the regenerator, and the second outlet of which is connected to the second bypass line, for adjusting the refrigerant flow ratio through the low-temperature side passage of the regenerator.

[0012] According to one embodiment of the present invention, in the regenerator, the flow direction of the refrigerant flowing through the high-temperature side channel is opposite to the flow direction of the refrigerant flowing through the low-temperature side channel.

[0013] A second aspect of the present invention provides a compressor performance testing method, comprising: The heat exchange step involves exchanging heat between the high-temperature refrigerant discharged from the compressor under test and the low-temperature refrigerant flowing out from the throttling device, in order to pre-cool the high-temperature refrigerant and preheat the low-temperature refrigerant. In the condensation step, the pre-cooled high-temperature refrigerant is fed into the condenser for condensation. In the evaporation step, the preheated cryogenic refrigerant is fed into an evaporator for evaporation.

[0014] According to one embodiment of the present invention, the compressor performance testing method further includes: When testing operating conditions with a large cooling capacity range, the heat exchange step described above is performed; When testing operating conditions within a small cooling capacity range, the high-temperature refrigerant discharged from the compressor under test is directly introduced into the condenser.

[0015] According to an embodiment of the present invention, the compressor performance testing method further includes a flow calibration step, the flow calibration step comprising: Measure the flow rate, inlet parameters, and outlet parameters of the cooling medium flowing through the subcooler; Measure the inlet parameters of the refrigerant before it enters the subcooler and the outlet parameters after it leaves the subcooler; Based on the principle of energy conservation, the total heat absorbed by the cooling medium in the subcooler is calculated according to the measured parameters, and the specific enthalpy difference of the refrigerant before and after flowing through the subcooler is calculated according to the measured parameters. The theoretical flow rate of the refrigerant is calculated by dividing the total heat by the specific enthalpy difference; and The theoretical flow rate is compared with the flow rate measured by the flow meter to calibrate the flow meter.

[0016] According to one embodiment of the present invention, the compressor performance testing method further includes at least one of the following control steps: The exhaust pressure is controlled by adjusting the exhaust throttle valve located at the exhaust port of the compressor under test; The intake pressure is controlled by adjusting the opening of the throttling device; The intake temperature is controlled by adjusting the power applied to the evaporator; The pressure and / or temperature of the refrigerant at the outlet of the condenser are controlled by adjusting a two-way regulating valve or a proportional three-way valve installed on the cooling water circuit of the condenser.

[0017] The compressor performance testing device provided in this embodiment of the invention recovers internal heat through a regenerator, which reduces the heat load of the condenser and the cold load of the evaporator, reduces the energy consumption and capacity requirements of external auxiliary temperature control equipment, and lowers testing costs. High-temperature refrigerant is pre-cooled before entering the condenser, reducing the condenser's heat exchange pressure; low-temperature refrigerant is pre-heated before entering the evaporator, improving the stability of the evaporation process and preventing test fluctuations caused by liquid refrigerant flash. With the same auxiliary temperature control system configuration, compressors with higher power and a wider cooling capacity range can be tested, broadening the applicability of the testing device.

[0018] According to the second aspect of the present invention, the compressor performance testing method can pre-lower the temperature of the high-temperature refrigerant before the refrigerant enters the condenser, thereby reducing the heat load of the condenser. At the same time, it can pre-raise the temperature of the low-temperature refrigerant before the refrigerant enters the evaporator, thereby stabilizing the operating conditions of the evaporation process, making the evaporation process more stable and controllable, and improving the stability of the compressor performance testing process and the accuracy of the test results.

[0019] According to one embodiment of the present invention, the compressor performance testing device can perform compressor performance testing while also being compatible with plate heat exchanger performance testing, thus possessing multi-functional integrated testing capabilities. Specifically: When the plate heat exchanger under test is connected to the condenser side, the heat transfer can be calculated by measuring the temperature changes and flow parameters of the refrigerant at the condenser inlet and subcooler inlet, as well as the inlet and outlet temperatures and flow parameters of the cooling medium on the condenser water side, combined with the heat exchange area of ​​the plate heat exchanger. Furthermore, the overall heat transfer coefficient of the plate heat exchanger can be calculated using the logarithmic mean temperature difference method. This function enables the testing device to not only perform compressor performance testing but also measure heat exchanger performance, thereby significantly improving the integration and utilization efficiency of the device. Attached Figure Description

[0020] To more clearly illustrate the technical solutions in this invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0021] Figure 1 This is a schematic diagram of the first compressor performance testing device provided by the present invention.

[0022] Figure 2 This is a schematic diagram of the second compressor performance testing device provided by the present invention.

[0023] Figure 3This is a schematic diagram of the third compressor performance testing device provided by the present invention.

[0024] Figure 4 This is a schematic diagram illustrating the principle of pressure / temperature control before the subcooler provided by the present invention.

[0025] Figure 5 This is a schematic diagram of the compressor performance testing device with plate heat exchanger testing function provided by the present invention.

[0026] Figure 6 This is a schematic flowchart of the compressor performance testing method provided by the present invention.

[0027] Figure label: 100. Condenser; 102. Throttling device; 104. Evaporator; 106. Regenerator; 108. Subcooler; 110. Flow meter; 112. Sensor; 114. Proportional three-way valve; 116. Solenoid valve; 118. Two-way regulating valve. Detailed Implementation

[0028] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0029] The specific terms used in this specification are for illustrative purposes only and are not intended to limit the illustrated embodiments. For example, expressions such as "same" and "identical" not only indicate a strictly identical state, but also indicate a state with tolerances or differences in the degree of functionality. For example, expressions indicating relative or absolute arrangement such as "in a certain direction," "along a certain direction," "side by side," "perpendicular," "centered on," "concentric," or "coaxial" not only strictly indicate such an arrangement, but also indicate a state of relative displacement by tolerances or angles or distances with the same degree of functionality.

[0030] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" 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 simplifying the description, and are not intended to 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.

[0031] Furthermore, features specified as "first" or "second" may explicitly or implicitly include one or more of those features. In the description of this invention, unless otherwise stated, "multiple" means two or more. In the description of the embodiments of this application, "multiple" means two or more, unless otherwise explicitly specified. In the description of the embodiments of this application, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, B1 and / or B2 can represent: B1 existing alone, B1 and B2 existing simultaneously, and B2 existing alone. Additionally, the character " / " in this document generally indicates that the preceding and following related objects have an "or" relationship.

[0032] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0033] like Figures 1 to 5 As shown, a first aspect of the present invention provides a compressor performance testing device, including a compressor under test, a condenser 100, a throttling device 102, and an evaporator 104. The discharge port of the compressor under test, the condenser 100, the throttling device 102, the evaporator 104, and the suction port of the compressor under test are sequentially connected by pipelines to form a refrigerant circulation loop. The device also includes a regenerator 106, which has a high-temperature side channel and a low-temperature side channel. The high-temperature side channel is connected in series between the discharge port of the compressor under test and the inlet of the condenser 100, and the low-temperature side channel is connected in series between the outlet of the throttling device 102 and the inlet of the evaporator 104.

[0034] According to the compressor performance testing device provided in the embodiments of the present invention, internal heat recovery is achieved through the regenerator 106, which can reduce the heat load of the condenser 100 and the cold load of the evaporator 104, reduce the energy consumption and capacity requirements of the external auxiliary temperature control equipment, and reduce testing costs; the high-temperature refrigerant is pre-cooled before entering the condenser 100, reducing the heat exchange pressure of the condenser 100, and the low-temperature refrigerant is pre-heated before entering the evaporator 104, improving the stability of the evaporation process and avoiding test fluctuations caused by liquid refrigerant flashing; under the same auxiliary temperature control system configuration, compressors with higher power and a wider range of cooling capacity can be tested, broadening the applicability of the testing device.

[0035] Please continue reading Figures 1 to 5The discharge port of the compressor under test, condenser 100, throttling device 102, evaporator 104, and suction port of the compressor under test are sequentially connected by pipelines to form a closed refrigerant circulation loop. The regenerator 106 is a heat exchange component, internally equipped with independent high-temperature and low-temperature channels for heat exchange. The high-temperature channel is connected in series to the pipeline between the discharge port of the compressor under test and the inlet of the condenser 100, used for the flow of high-temperature, high-pressure refrigerant discharged from the compressor under test; the low-temperature channel is connected in series to the pipeline between the outlet of the throttling device 102 and the inlet of the evaporator 104, used for the flow of low-temperature, low-pressure refrigerant after throttling. The refrigerants in the high-temperature and low-temperature channels exchange heat indirectly through the wall of the regenerator 106, achieving pre-cooling of the high-temperature refrigerant and preheating of the low-temperature refrigerant.

[0036] According to one embodiment of the present invention, the device further includes a subcooler 108 and a flow meter 110. The subcooler 108 is disposed between the outlet of the condenser 100 and the inlet of the throttling element 102, and the flow meter 110 is used to measure the flow rate of refrigerant flowing through the subcooler 108.

[0037] In one embodiment of the present invention, the subcooler 108 is a shell-and-tube heat exchanger, which has a refrigerant channel and a cooling medium channel inside. The refrigerant channel is connected between the outlet of the condenser 100 and the inlet of the throttling device 102. The cooling medium channel is connected to an external cooling source. The refrigerant inlet of the subcooler 108 is sealed to the outlet of the condenser 100 through a pipe, and the outlet is sealed to the inlet of the throttling device 102 through a pipe. The flow meter 110 is an electromagnetic flow meter 110, which is installed on the refrigerant channel of the subcooler 108 to directly measure the volumetric flow rate of the refrigerant flowing through the subcooler 108. The sensor 112 part of the flow meter 110 is flush with the inner wall of the pipe, so as not to generate additional resistance, and has high accuracy and real-time data output function.

[0038] This structure adds a subcooler 108 between the condenser 100 and the throttling device 102, further cooling the high-pressure liquid refrigerant to a subcooled state before it enters the throttling device 102. This effectively prevents the generation of flash vapor, improves system stability and testing accuracy, and allows the flow meter 110 to continuously monitor the refrigerant flow before and after the subcooler 108, providing real-time flow data for the system. Combined with the inlet and outlet temperatures and flow rates of the cooling medium, the theoretical flow rate can be calculated through energy conservation. This theoretical flow rate is then used for real-time calibration with the flow meter 110 reading, improving the accuracy and reliability of flow measurement and providing a precise basis for calculating the compressor's cooling capacity.

[0039] According to one embodiment of the present invention, the subcooler 108 has a refrigerant passage and a cooling medium passage; the compressor performance testing device further includes a sensor 112 for measuring parameters of the cooling medium flowing through the cooling medium passage, for calculating the refrigerant flow rate and calibrating it with the reading of the flow meter 110.

[0040] In one embodiment of the present invention, the cooling medium channel of the subcooler 108 is a closed loop, with its inlet connected to an external cooling water source and its outlet connected to a cooling return water pipe. A temperature sensor 112 and a flow sensor 112 are installed within the cooling medium channel. The temperature sensor 112 is installed at the inlet and outlet of the cooling medium channel to collect the inlet and outlet temperatures of the cooling medium in real time. The flow sensor 112 is installed on the main flow path of the cooling medium channel to measure the real-time flow rate of the cooling medium. All sensors 112 are connected to the central control unit via signal lines. The control unit calculates the total heat absorbed by the refrigerant in the subcooler 108 using the energy balance equation based on the inlet temperature, outlet temperature, flow rate of the cooling medium, and the heat exchange area and heat transfer coefficient of the subcooler 108. Based on this, it calculates the mass flow rate of the refrigerant. This calculation result is compared with the measured value of the flow meter 110 to determine the measurement deviation of the flow meter 110 and to perform dynamic correction.

[0041] This design establishes a dual verification mechanism for flow measurement by introducing parameter measurement and theoretical calculation of the cooling medium. This effectively overcomes the measurement error problem caused by wear, blockage, or calibration drift of a single flow meter 110, and realizes online real-time verification and adaptive correction of flow data. This greatly improves the measurement accuracy and long-term stability of the test system for refrigerant flow, and provides a reliable data foundation for the accurate evaluation of key parameters such as compressor performance coefficient and cooling capacity.

[0042] like Figure 4 As shown, according to one embodiment of the present invention, the compressor performance testing device further includes a regulating valve disposed on the cooling water circuit of the condenser 100 and a sensor disposed at the outlet of the condenser 100. The sensor is signal-connected to a PID controller, and the output of the PID controller is signal-connected to the regulating valve to control the pressure and / or temperature of the refrigerant at the outlet of the condenser 100. Specifically, it includes the following two implementation schemes: Option 1: A two-way regulating valve 118 is installed on the cooling water circuit of condenser 100. A pressure sensor and a high-precision temperature sensor are installed on the refrigerant outlet side of condenser 100. The sensors collect the pressure and temperature of the refrigerant at the outlet of condenser 100 in real time and feed them back to the PID controller. The PID controller outputs a control signal to the two-way regulating valve 118 based on the deviation, adjusting its opening to change the cooling water flow rate, thereby controlling the pressure and temperature of the refrigerant at the outlet of condenser 100. When the outlet pressure or temperature is higher than the set value, the valve opening is increased to increase the cooling water flow rate and enhance heat exchange; conversely, the opening is decreased. This option has a simple structure, fast response speed, and is suitable for operating conditions where the cooling water source temperature is relatively stable.

[0043] Option 2: A three-way regulating valve 114 is installed on the cooling water circuit of condenser 100. The three ports of the three-way regulating valve 114 are connected to the cooling water supply pipeline, the cooling water return pipeline of condenser 100, and the cooling water inlet pipeline of condenser 100, respectively. A temperature sensor is installed on the refrigerant outlet side of condenser 100. The temperature sensor feeds the signal back to the PID controller. The PID controller outputs a control signal to the three-way regulating valve to adjust the mixing ratio of chilled water and return water, thereby changing the temperature of the cooling water entering condenser 100 and thus controlling the temperature of the refrigerant at the outlet of condenser 100. This option offers high control precision, avoids system fluctuations caused by changes in water flow, and is suitable for precision testing conditions requiring high stability of condensing temperature.

[0044] The two schemes mentioned above can be flexibly selected according to actual testing needs. Scheme 1 directly changes the heat exchange by adjusting the water flow rate, while Scheme 2 achieves a more stable heat exchange process under constant flow conditions by mixing water and adjusting the temperature. The two complement each other and jointly improve the control accuracy and applicability of the testing device.

[0045] like Figure 5 As shown, in one embodiment of the present invention, the compressor performance testing device also has a plate heat exchanger performance testing function. Specifically, corresponding reserved interfaces are respectively provided on the inlet and outlet sides of the condenser 100 on the refrigerant side and the cooling water side. The reserved interfaces can be selectively connected to an external plate heat exchanger through valve assemblies, so that the plate heat exchanger to be tested is connected to the original refrigerant circulation loop, and the solenoid valves on the inlet and outlet sides of the condenser 100 on the refrigerant side and the cooling water side are closed to test the plate heat exchanger to be tested.

[0046] Furthermore, a first temperature measuring point is provided at the inlet of the condenser 100, and a second temperature measuring point is provided at the inlet of the subcooler 108, for obtaining temperature parameters before and after heat exchange on the refrigerant side; at the same time, temperature sensors are respectively provided at the inlet and outlet of the cooling water channel of the condenser 100 for measuring the inlet and outlet temperatures of the cooling medium in real time.

[0047] Similarly, an interface can be reserved on the evaporator side, and cooling water can be introduced from the reserved interface in the water circuit for plate heat exchanger testing.

[0048] With the above structural setup, the heat exchange performance of external plate heat exchangers can be tested without changing the original compressor test circuit, giving the device multifunctional testing capabilities.

[0049] According to one embodiment of the present invention, it further includes: The first bypass pipeline is connected in parallel with the high-temperature side channel of the regenerator 106; The second bypass pipeline is connected in parallel with the low-temperature side channel of the regenerator 106; A valve assembly is used to control the selective flow of refrigerant through the regenerator 106 or through the first bypass line and the second bypass line.

[0050] In one embodiment of the present invention, the first bypass pipeline is an independent pipe, one end of which is connected to the node between the exhaust port of the compressor under test and the inlet of the high-temperature side channel of the regenerator 106, and the other end of which is connected to the node between the outlet of the high-temperature side channel of the regenerator 106 and the inlet of the condenser 100, forming a passage in parallel with the high-temperature side channel. The second bypass pipeline is another independent pipe, one end of which is connected to the node between the outlet of the throttling device 102 and the inlet of the low-temperature side channel of the regenerator 106, and the other end of which is connected to the node between the outlet of the low-temperature side channel of the regenerator 106 and the inlet of the evaporator 104, forming a passage in parallel with the low-temperature side channel. The valve assembly is an integrated control valve group, which includes multiple electric valves or solenoid valves 116. The refrigerant flow direction is selected through logic control. When the valve assembly is closed, all the refrigerant flows through the regenerator 106. When the valve assembly is open, part of the refrigerant bypasses the regenerator 106 and directly enters the subsequent components through the first bypass pipeline and the second bypass pipeline, realizing the opening and closing of the regeneration function.

[0051] This bypass structure gives the testing device a flexible operating condition switching capability, allowing the system to dynamically adjust whether to enable the reheat function according to the testing requirements. It is especially suitable for situations where reheat needs to be enabled to save energy and reduce consumption under high cooling capacity conditions, and for situations where reheat needs to be turned off under low cooling capacity conditions to avoid excessive preheating and excessive intake superheat. This expands the applicability of the device, improves testing flexibility and safety, and provides technical support for performance comparison analysis under different testing modes.

[0052] According to one embodiment of the present invention, the valve assembly includes a proportional three-way valve 114, the inlet of which is connected to the outlet of the throttling element 102, the first outlet of which is connected to the low-temperature side passage of the regenerator 106, and the second outlet of which is connected to a second bypass line for adjusting the refrigerant flow ratio through the low-temperature side passage of the regenerator 106.

[0053] In one embodiment of the present invention, the proportional three-way valve 114 is a valve with continuously adjustable opening. Its inlet end is connected to the outlet pipe of the throttling element 102, the first outlet end is connected to the inlet pipe of the low-temperature side channel of the regenerator 106, and the second outlet end is connected to the inlet pipe of the second bypass pipe. The proportional three-way valve 114 is provided with a rotatable valve core. By adjusting the position of the valve core through the controller, the flow area of ​​each outlet is changed, thereby precisely controlling the proportion of refrigerant flow entering the low-temperature side channel of the regenerator 106. For example, when the valve core is deflected to a certain angle, 60% of the refrigerant flows into the regenerator 106, and 40% of the refrigerant directly enters the evaporator 104 through the bypass. This adjustment process can be carried out in real time during the test without stopping the machine to replace the pipeline, thus realizing dynamic adjustment.

[0054] The proportional three-way valve 114 can precisely regulate the refrigerant flow into the regenerator 106, achieving fine adjustment of the regeneration intensity. This allows the system to automatically optimize the regeneration effect according to actual test conditions (such as different pressure ratios and different refrigerant types), avoiding performance deviations caused by excessive or insufficient regeneration. It is particularly suitable for test scenarios that require precise control of suction temperature, improving the repeatability and consistency of test data, while simplifying the system operation process and increasing test efficiency.

[0055] According to one embodiment of the present invention, in the regenerator 106, the flow direction of the refrigerant flowing through the high-temperature side channel is opposite to the flow direction of the refrigerant flowing through the low-temperature side channel.

[0056] In one embodiment of the present invention, the high-temperature side channel and the low-temperature side channel inside the regenerator 106 are arranged in a counter-current manner, that is, the direction of refrigerant flow from the inlet to the outlet in the high-temperature side channel is completely opposite to the direction of refrigerant flow from the inlet to the outlet in the low-temperature side channel. The two form the maximum temperature difference distribution in the heat exchange area, so that the average temperature difference during the heat exchange process reaches the maximum value, thereby improving the heat transfer efficiency. The entire flow path inside the regenerator 106 is guided by the flow divider plate, the guide plate and the baffle structure to ensure that the two fluids do not cross each other in space but are in full contact, thereby achieving efficient heat exchange.

[0057] This counter-current arrangement significantly improves the heat exchange efficiency of the regenerator 106, making the heat transfer between the high-temperature exhaust and the low-temperature refrigerant more complete, shortening the time required to reach the target pre-cooling and pre-heating temperatures, reducing energy loss, improving the overall energy efficiency of the system, and avoiding local overheating or overcooling, ensuring the stability of the testing process and the reliability of the data. It is a key structural design for achieving efficient energy recovery.

[0058] like Figure 6 As shown, a second aspect of the present invention provides a compressor performance testing method, comprising: The heat exchange step involves exchanging heat between the high-temperature refrigerant discharged from the compressor under test and the low-temperature refrigerant flowing out from the throttling device 102, in order to pre-cool the high-temperature refrigerant and preheat the low-temperature refrigerant. In the condensation step, the pre-cooled high-temperature refrigerant is sent into the condenser 100 for condensation; In the evaporation step, the preheated low-temperature refrigerant is fed into the evaporator 104 for evaporation.

[0059] According to the second aspect of the present invention, the compressor performance testing method can pre-lower the temperature of the high-temperature refrigerant before the refrigerant enters the condenser 100, thereby reducing the heat load of the condenser 100. At the same time, it can pre-raise the temperature of the low-temperature refrigerant before the refrigerant enters the evaporator 104, thereby stabilizing the operating conditions of the evaporation process, making the evaporation process more stable and controllable, and improving the stability of the compressor performance testing process and the accuracy of the test results.

[0060] A second aspect of the present invention provides a compressor performance testing method, comprising: a heat exchange step, wherein a high-temperature refrigerant discharged from the compressor under test is exchanged with a low-temperature refrigerant flowing out from a throttling device 102 to pre-cool the high-temperature refrigerant and preheat the low-temperature refrigerant; a condensation step, wherein the pre-cooled high-temperature refrigerant is fed into a condenser 100 for condensation; and an evaporation step, wherein the preheated low-temperature refrigerant is fed into an evaporator 104 for evaporation.

[0061] The heat exchange step is achieved by setting up a regenerator 106 in the refrigerant circuit. The high-temperature refrigerant discharged from the compressor under test flows through the high-temperature side channel of the regenerator 106, and the low-temperature refrigerant flowing out of the throttling device 102 flows through the low-temperature side channel of the regenerator 106. The high-temperature refrigerant and the low-temperature refrigerant undergo non-contact indirect heat exchange in the regenerator 106, thereby achieving pre-cooling of the high-temperature refrigerant and preheating of the low-temperature refrigerant.

[0062] According to one embodiment of the present invention, the compressor performance testing method further includes: When testing operating conditions with a large cooling capacity range, perform a heat exchange step; When testing operating conditions within a small cooling capacity range, the high-temperature refrigerant discharged from the compressor under test is directly introduced into the condenser 100.

[0063] In one embodiment of the present invention, when testing operating conditions with a large cooling capacity range, the system activates the regeneration function, controls the valve assembly to allow the refrigerant to flow through the high-temperature side channel and the low-temperature side channel of the regenerator 106, and performs a heat exchange step, that is, the high-temperature exhaust gas and the low-temperature refrigerant exchange heat in a countercurrent manner to achieve pre-cooling and preheating. Then, the pre-cooled high-temperature refrigerant is sent to the condenser 100 for condensation. When testing operating conditions with a small cooling capacity range, the system deactivates the regeneration function, controls the valve assembly to allow the high-temperature refrigerant discharged from the compressor under test to bypass the regenerator 106 and directly enter the condenser 100 through the first bypass pipeline. At this time, the regenerator 106 is in a bypass state and does not participate in heat exchange, but only exists as a bypass channel, thereby avoiding excessive superheat of the suction gas caused by regeneration and ensuring that the test conditions meet the operating requirements of the small cooling capacity operating conditions.

[0064] This dual-mode switching strategy enables intelligent adaptation to test conditions. For high-capacity cooling conditions, regeneration is activated to reduce the load on the auxiliary temperature control system, achieving energy saving and consumption reduction. For low-capacity cooling conditions, regeneration is turned off to prevent overheating, ensuring that the compressor suction temperature is within a safe range, avoiding liquid slugging or abnormal operation, improving the safety and effectiveness of the test, and enabling the same test device to cover a wide range of compressor cooling capacity test needs, significantly improving the utilization rate and economy of the equipment.

[0065] According to one embodiment of the present invention, the compressor performance testing method further includes a flow calibration step, which includes: Measure the flow rate, inlet parameters, and outlet parameters of the cooling medium flowing through cooler 108; Measure the inlet parameters of the refrigerant before it enters the subcooler 108 and the outlet parameters after it leaves the subcooler 108. Based on the principle of energy conservation, the total heat absorbed by the cooling medium in the subcooler 108 is calculated according to the measured parameters, and the specific enthalpy difference of the refrigerant before and after flowing through the subcooler 108 is calculated according to the measured parameters. Dividing the total heat by the specific enthalpy difference yields the theoretical flow rate of the refrigerant; and The theoretical flow rate is compared with the flow rate measured by flow meter 110 to calibrate flow meter 110.

[0066] In one embodiment of the present invention, before the refrigerant enters the throttling device 102, it must first flow through the subcooler 108. The refrigerant channel and the cooling medium channel of the subcooler 108 exchange heat through a heat-conducting wall. The cooling medium is input from an external cooling source and flows through the cooling medium channel of the subcooler 108. Its inlet temperature, outlet temperature and flow rate are collected in real time by a sensor 112 installed in the cooling medium channel. The control system calculates the total heat absorbed by the refrigerant in the subcooler 108 based on the inlet temperature, outlet temperature, flow rate of the cooling medium and the heat exchange area and heat transfer coefficient of the subcooler 108 using the principle of energy conservation, and calculates the mass flow rate of the refrigerant accordingly. The calculation result is compared with the measured value of the flow meter 110. If there is a deviation, a calibration procedure is triggered to dynamically correct the measured value of the flow meter 110 to ensure the accuracy of the flow data.

[0067] This method constructs a dual verification mechanism for refrigerant flow rate through parameter measurement and theoretical calculation of the cooling medium. It effectively solves the problems of measurement drift or blockage caused by long-term use of traditional flow meter 110, realizes online real-time verification and adaptive correction of flow data, greatly improves the measurement accuracy and long-term stability of the test system for refrigerant flow rate, provides solid data support for the accurate evaluation of key parameters such as compressor performance coefficient and cooling capacity, and enhances the credibility and repeatability of test results.

[0068] According to one embodiment of the present invention, the compressor performance testing method further includes at least one of the following control steps: The exhaust pressure is controlled by adjusting the exhaust throttle valve located at the exhaust port of the compressor under test; The intake pressure is controlled by adjusting the opening of the throttle element 102; The intake temperature is controlled by adjusting the power applied to the evaporator 104.

[0069] In one embodiment of the present invention, an exhaust throttling valve is installed on the pipe between the exhaust port of the compressor under test and the inlet of the high-temperature side channel of the regenerator 106. By adjusting its opening, the flow resistance of the exhaust pipe can be changed, thereby adjusting the pressure of the compressor exhaust port and achieving precise control of the system exhaust pressure. The throttling element 102 is an electronic expansion valve or a manual regulating valve, which is installed on the pipe between the outlet of the subcooler 108 and the inlet of the evaporator 104. By adjusting its opening, the flow rate and pressure of the refrigerant after throttling can be changed, thereby controlling the suction pressure at the inlet of the evaporator 104. The evaporator 104 is an electrically heated evaporator with a heating element inside. By adjusting the electrical power applied to the heating element, the evaporation temperature inside the evaporator 104 can be controlled, thereby achieving precise adjustment of the refrigerant temperature entering the compressor suction port.

[0070] This multi-parameter collaborative control system enables the testing system to accurately simulate various operating conditions, meeting the testing requirements of different compressors. By adjusting the exhaust pressure through the exhaust throttle valve, high pressure ratio conditions can be simulated; by adjusting the opening of the throttle element 102 to control the suction pressure, performance testing under different pressure ratios can be achieved; by adjusting the power of the evaporator 104 to control the suction temperature, the suction superheat can be precisely set, ensuring the safety of the testing process and the accuracy of the data, and improving the versatility and intelligence level of the testing device.

[0071] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A compressor performance testing device, comprising a compressor under test, a condenser, a throttling element, and an evaporator, wherein, The exhaust port of the compressor under test, the condenser, the throttling device, the evaporator, and the suction port of the compressor under test are sequentially connected by pipelines to form a refrigerant circulation loop. The feature is that it also includes a regenerator, which has a high-temperature side channel and a low-temperature side channel. The high-temperature side channel is connected in series between the exhaust port of the compressor under test and the inlet of the condenser, and the low-temperature side channel is connected in series between the outlet of the throttling device and the inlet of the evaporator.

2. The compressor performance testing device according to claim 1, characterized in that, It also includes a subcooler and a flow meter. The subcooler is disposed between the outlet of the condenser and the inlet of the throttling element, and the flow meter is used to measure the refrigerant flow rate through the subcooler. The subcooler has a refrigerant passage and a cooling medium passage; the compressor performance testing device also includes a sensor for measuring the parameters of the cooling medium flowing through the cooling medium passage, in order to calculate the refrigerant flow rate and calibrate it with the reading of the flow meter.

3. The compressor performance testing device according to claim 1, characterized in that, It also includes an installation passage for connecting to the plate heat exchanger under test, wherein the installation passage is located at the inlet and outlet of the refrigerant side and the cooling water side of the condenser for connecting the external plate heat exchanger; The installation path includes a temperature sensor for measuring the temperature of the refrigerant as it enters and exits the condenser. The temperature sensor is located at the inlet and outlet of the cooling water channel of the condenser. The temperature sensor is also used to measure the inlet and outlet temperatures of the cooling water to calculate the heat exchange and heat transfer coefficient.

4. The compressor performance testing device according to claim 1, characterized in that, Also includes: The first bypass pipeline is connected in parallel with the high-temperature side channel of the regenerator; The second bypass pipeline is connected in parallel with the low-temperature side channel of the regenerator; A valve assembly for controlling the selective flow of refrigerant through the regenerator or through the first bypass line and the second bypass line.

5. The compressor performance testing device according to claim 4, characterized in that, The valve assembly includes a proportional three-way valve, the inlet of which is connected to the outlet of the throttling element, the first outlet of which is connected to the low-temperature side channel of the regenerator, and the second outlet of which is connected to the second bypass line, for adjusting the refrigerant flow ratio through the low-temperature side channel of the regenerator.

6. The compressor performance testing device according to claim 1, characterized in that, In the regenerator, the refrigerant flowing through the high-temperature side channel flows in the opposite direction to the refrigerant flowing through the low-temperature side channel.

7. A method for testing the performance of a compressor, characterized in that, include: The heat exchange step involves exchanging heat between the high-temperature refrigerant discharged from the compressor under test and the low-temperature refrigerant flowing out from the throttling device, in order to pre-cool the high-temperature refrigerant and preheat the low-temperature refrigerant. In the condensation step, the pre-cooled high-temperature refrigerant is fed into the condenser for condensation. In the evaporation step, the preheated cryogenic refrigerant is fed into an evaporator for evaporation.

8. The compressor performance testing method according to claim 7, characterized in that, The compressor performance testing method also includes: When testing operating conditions with a large cooling capacity range, the heat exchange step described above is performed; When testing operating conditions within a small cooling capacity range, the high-temperature refrigerant discharged from the compressor under test is directly introduced into the condenser.

9. The compressor performance testing method according to claim 7, characterized in that, The compressor performance testing method further includes a flow calibration step, which includes: Measure the flow rate, inlet parameters, and outlet parameters of the cooling medium flowing through the subcooler; Measure the inlet parameters of the refrigerant before it enters the subcooler and the outlet parameters after it leaves the subcooler; Based on the principle of energy conservation, the total heat absorbed by the cooling medium in the subcooler is calculated according to the measured parameters, and the specific enthalpy difference of the refrigerant before and after flowing through the subcooler is calculated according to the measured parameters. The theoretical flow rate of the refrigerant is calculated by dividing the total heat by the specific enthalpy difference; and The theoretical flow rate is compared with the flow rate measured by the flow meter to calibrate the flow meter.

10. The compressor performance testing method according to claim 7, characterized in that, The compressor performance testing method further includes at least one of the following control steps: The exhaust pressure is controlled by adjusting the exhaust throttle valve located at the exhaust port of the compressor under test; The intake pressure is controlled by adjusting the opening of the throttling device; The intake temperature is controlled by adjusting the power applied to the evaporator; The pressure and / or temperature of the refrigerant at the outlet of the condenser are controlled by adjusting a two-way regulating valve or a proportional three-way valve installed on the cooling water circuit of the condenser.

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