Full dynamic pressure type air refrigeration system test system
By designing a fully dynamic pressure air refrigeration system test system, the lack of performance testing for novel air reverse Brayton cycle refrigeration systems was solved, enabling performance testing of centrifugal compressors and turbine expanders, and improving the convenience and efficiency of testing.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- QICHENG SUSPENSION TECHNOLOGY (NANTONG) CO LTD
- Filing Date
- 2025-06-23
- Publication Date
- 2026-04-24
AI Technical Summary
The lack of a dedicated system for testing the performance of novel air-to-breton cycle refrigeration systems limits their application and optimization in distributed refrigeration scenarios.
A fully dynamic pressure air refrigeration system test system was designed, including a test bench, a centrifugal compressor and a turbo expander. Performance testing is carried out through connecting pipelines and detection elements, supporting different combinations and variable operating conditions.
It enables performance testing of centrifugal compressors and turboexpanders, improving the convenience and efficiency of testing while reducing labor intensity and costs.
Smart Images
Figure CN224163378U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the technical field of air refrigeration testing systems, and in particular to a fully dynamic pressure air refrigeration system testing system. Background Technology
[0002] Currently, refrigeration equipment is widely used in homes, businesses, and industries, and most of it adopts the mature vapor compression refrigeration principle. Although this principle is technologically mature and widely used, its operation depends on refrigerants, which to some extent limits its sustainable development.
[0003] Combining air with the reverse Brayton cycle for refrigeration not only effectively avoids the use of traditional refrigerants but also significantly reduces energy consumption, showing broad application prospects. However, traditional reverse Brayton cycle refrigeration systems typically use screw compressors as the core component. While screw compressors offer stable performance, their large size and high weight make them difficult to apply flexibly in many distributed refrigeration scenarios, limiting the promotion and use of reverse Brayton cycle refrigeration systems.
[0004] In recent years, with the continuous development and gradual maturation of centrifugal compressor technology, the application of centrifugal compressors in air reverse Brayton cycle refrigeration systems to replace traditional screw compressors has made the application of air reverse Brayton cycle refrigeration systems in distributed refrigeration scenarios more feasible, demonstrating great development potential.
[0005] However, there is currently a lack of a dedicated system on the market for testing the performance of this novel air-cooling system. Developing a testing system capable of accurately and comprehensively testing the performance of this new air-cooling system is of paramount importance for optimizing system design, improving system efficiency, and promoting the widespread application of this new air-cooling technology.
[0006] To address this, a test system for a fully dynamic pressure air refrigeration system is proposed. Utility Model Content
[0007] The purpose of this invention is to provide a testing system for a fully dynamic pressure air refrigeration system, which aims to solve or improve at least one of the above-mentioned technical problems.
[0008] To achieve the above objectives, the present invention provides the following solution: The present invention provides a test system for a fully dynamic pressure air refrigeration system, including a test bench, on which a centrifugal compressor and a turbo expander are detachably connected. The exhaust end of the centrifugal compressor and the intake end of the turbo expander are connected through a first connecting pipe. A pressure regulating valve is provided on the first connecting pipe. The intake end of the centrifugal compressor is detachably connected to a compressor intake pipe, and the exhaust end of the turbo expander is detachably connected to a turbo expander exhaust pipe.
[0009] A first pressure detection element and a first temperature detection element are provided on the compressor intake pipe and on the first connecting pipe near the centrifugal compressor exhaust end. A second pressure detection element and a second temperature detection element are provided on the turbine expander exhaust pipe and on the first connecting pipe near the turbine expander intake end. The pressure regulating valve is located between the first pressure detection element at the centrifugal compressor exhaust end and the second pressure detection element at the turbine expander intake end.
[0010] Preferably, the first connecting pipeline includes a compressor exhaust pipeline, a heat dissipation pipeline, a reversing pipeline, and a turbine intake pipeline connected in sequence. The exhaust end of the centrifugal compressor is sealed to the compressor exhaust pipeline via a hose and a clamp. The turbine intake pipeline is sealed to the intake end of the turbine expander via a flange joint. The pressure regulating valve is located between the reversing pipeline and the turbine intake pipeline. A first pressure detection element and a first temperature detection element at the exhaust end of the centrifugal compressor are installed on the compressor exhaust pipeline. A second pressure detection element and a second temperature detection element at the intake end of the turbine expander are installed on the turbine intake pipeline.
[0011] Preferably, the compressor exhaust pipe is connected to the heat dissipation pipe via a threaded connection, the end of the heat dissipation pipe away from the compressor exhaust pipe is connected to the first flow meter via a flange joint, and the end of the first flow meter away from the heat dissipation pipe is connected to the reversing pipe via a flange joint.
[0012] Preferably, a three-way valve is sealed between the reversing pipeline and the turbine intake pipeline via a flange joint, the third port of the three-way valve is sealed to the pressure regulating valve via a flange joint, and the end of the pressure regulating valve away from the three-way valve is sealed to the muffler.
[0013] Preferably, the turbine expander exhaust pipe is sealed to the second flow meter via a flange joint.
[0014] Preferably, an air filter is fixedly connected to the frame, and the exhaust end of the air filter is sealed to the compressor intake pipe through a hose and a clamp. The end of the compressor intake pipe away from the air filter is sealed to the intake end of the centrifugal compressor through a hose and a clamp.
[0015] Preferably, a plurality of heat dissipation fins are fixedly attached to the outer wall of the heat dissipation pipe.
[0016] Preferably, a number of casters are fixed to the bottom of the platform.
[0017] This utility model discloses the following technical effects: The centrifugal compressor and the turboexpander are detachably connected to a test bench, and the exhaust end of the centrifugal compressor is connected to the intake end of the turboexpander via a first connecting pipe. During testing, the centrifugal compressor converts ambient temperature and pressure air into high temperature and high pressure air. The first pressure and temperature sensing elements at the intake and exhaust ends of the centrifugal compressor respectively detect the air pressure and temperature during intake and exhaust. The high temperature and high pressure air output from the centrifugal compressor is input into the turboexpander, and the second pressure and temperature sensing elements at the intake and exhaust ends of the turboexpander respectively detect the air pressure and temperature during intake and exhaust. This allows for simultaneous performance testing of both the centrifugal compressor and the turboexpander. Furthermore, different combinations of centrifugal compressors and turboexpanders can be used for testing, and the intake air pressure of the turboexpander can be changed by altering the opening of the regulating valve, thus enabling variable operating condition performance testing of the system.
[0018] This invention enables performance testing of centrifugal compressors and turboexpanders, is highly versatile, improves the convenience of refrigeration system testing, increases testing efficiency, and reduces labor intensity and costs. Attached Figure Description
[0019] The accompanying drawings, which form part of this application, are used to provide a further understanding of this application. The illustrative embodiments and descriptions of this application are used to explain this application and do not constitute an undue limitation of this application. In the drawings:
[0020] Figure 1 This is a schematic diagram of the structure of this utility model.
[0021] In the diagram: 1. Compressor intake pipe; 2. Centrifugal compressor; 3. Turbine expander; 4. Stand; 5. First flow meter; 6. Reversing pipe; 7. Pressure regulating valve; 8. Silencer; 9. Radiator pipe; 10. Turbine intake pipe; 11. Second flow meter; 12. Compressor exhaust pipe; 13. Air filter; 14. Electrical control cabinet; 15. Fuma wheel. Detailed Implementation
[0022] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.
[0023] To make the above-mentioned objectives, features and advantages of this utility model more apparent and understandable, the utility model will be further described in detail below with reference to the accompanying drawings and specific embodiments.
[0024] Reference Figure 1 This utility model provides a test system for a fully dynamic pressure air refrigeration system, including a test bench 4. A centrifugal compressor 2 and a turbine expander 3 are detachably connected to the test bench 4. The exhaust end of the centrifugal compressor 2 and the intake end of the turbine expander 3 are connected through a first connecting pipe. A pressure regulating valve 7 is provided on the first connecting pipe. The intake end of the centrifugal compressor 2 is detachably connected to a compressor intake pipe 1, and the exhaust end of the turbine expander 3 is detachably connected to a turbine expander exhaust pipe.
[0025] A first pressure detection element and a first temperature detection element are provided on the compressor intake pipe 1 and on the first connecting pipe near the exhaust end of the centrifugal compressor 2. A second pressure detection element and a second temperature detection element are provided on the turbine expander exhaust pipe and on the first connecting pipe near the intake end of the turbine expander 3. The pressure regulating valve 7 is located between the first pressure detection element at the exhaust end of the centrifugal compressor 2 and the second pressure detection element at the intake end of the turbine expander 3.
[0026] Furthermore, both the centrifugal compressor 2 and the turbine expander 3 are connected to the frame 4 by bolts, allowing for quick disassembly and installation.
[0027] Furthermore, both the centrifugal compressor 2 and the turbo expander 3 adopt fully dynamic pressure air suspension bearing technology. The radial bearing and the thrust bearing are both dynamic pressure air suspension bearings, which have the characteristics of being completely oil-free, zero-pollution, long service life, wide temperature range, low noise and strong robustness (the specifics are existing technologies and will not be elaborated here).
[0028] In some embodiments, both the first and second temperature sensing elements are temperature transmitters with data display capabilities. A temperature transmitter is an instrument that converts temperature variables into standardized, transmittable output signals. Thermocouples and resistance temperature detectors (RTDs) are used as temperature sensing elements. The output signal from the sensing element is sent to the transmitter module, where it undergoes processing through circuits such as voltage regulation and filtering, operational amplification, nonlinear correction, V / I conversion, constant current, and reverse protection. This processing converts the signal into a 4–20mA current signal or a 0-5V / 0-10V voltage signal that is linearly related to the temperature, and outputs an RS485 digital signal (specific details are existing technology and will not be elaborated here). The temperature in the pipeline can be detected by the temperature transmitter, and the displayed data can be recorded.
[0029] When installing a temperature transmitter, mounting holes need to be made in the installation pipeline (i.e., compressor inlet pipeline 1, first connecting pipeline, turbine expander exhaust pipeline, etc.). The probe of the temperature transmitter is inserted into the mounting hole and fixed, thereby collecting data on the gas temperature in the pipeline and displaying the measured data through an external display instrument. Specifically, the probe of the temperature transmitter can be selected with a threaded sleeve, in which case the mounting hole in the pipeline is a threaded hole, thus achieving a threaded connection. When selecting a probe without a fixing device, the probe can be directly inserted into the mounting hole and fixed by welding or adhesive bonding, depending on the actual situation. The temperature transmitter should be installed on a straight section of the pipeline, avoiding bends, valves, and other obstructing components to ensure measurement accuracy; the mounting hole in the pipeline must match the probe size.
[0030] In some embodiments, the first and second pressure sensing elements are selected from pressure transmitters with digital display functions. The pressure transmitter can convert the physical pressure parameters of gas, liquid, etc., sensed by the pressure sensing element sensors into standard electrical signals (such as 4-20mA DC), which are then supplied to secondary instruments such as indicators, alarms, recorders, and regulators for measurement and indication (specific details are prior art and will not be elaborated here). The pressure transmitter can detect the gas pressure in the pipeline and record the displayed data.
[0031] Pressure transmitters are installed on the corresponding pipelines, and can be connected by thread or welding. When choosing a threaded connection, a corresponding threaded hole needs to be drilled in the pipeline. The probe of the pressure transmitter has external threads, thus achieving the threaded connection. This connection method is robust, low-cost, and versatile. However, care must be taken to ensure thread compatibility during installation and disassembly to avoid damaging the threads. When choosing the welding method, the pressure transmitter's interface is butt-welded to the pipeline to form a permanent connection. This method provides a robust connection with good sealing and can withstand extreme operating conditions. However, installation and disassembly are more difficult, and once welded, modifications are challenging. The choice should be made based on the specific circumstances.
[0032] In some embodiments, the first temperature sensing element and the second temperature sensing element may be selected as temperature sensors, and the first pressure sensing element and the second pressure sensing element may be selected as pressure sensors, to measure the inlet pressure and temperature of the centrifugal compressor 2, the outlet pressure and temperature of the centrifugal compressor 2, the inlet pressure and temperature of the turbine expander 3, and the outlet pressure and temperature of the turbine expander 3; and an electrical control cabinet 14 is provided, which adopts a PLC controller with a data display screen. The limit signals measured by the pressure sensor and the temperature sensor are transmitted to the PLC controller, and the data is displayed and stored in real time.
[0033] In some optional embodiments, the first connecting pipeline includes a compressor exhaust pipeline 12, a heat dissipation pipe 9, a reversing pipeline 6, and a turbine intake pipeline 10 connected in sequence. The exhaust end of the centrifugal compressor 2 is sealed to the compressor exhaust pipeline 12 through a hose and a clamp. The turbine intake pipeline 10 is sealed to the intake end of the turbine expander 3 through a flange joint. The pressure regulating valve 7 is located between the reversing pipeline 6 and the turbine intake pipeline 10. The first pressure detection element and the first temperature detection element at the outlet end of the centrifugal compressor 2 are installed on the compressor exhaust pipeline 12. The second pressure detection element and the second temperature detection element at the intake end of the turbine expander 3 are installed on the turbine intake pipeline 10.
[0034] By installing a heat dissipation pipe 9 between the centrifugal compressor 2 and the turbine expander 3, the high-temperature and high-pressure air can be initially cooled.
[0035] Furthermore, the pressure regulating valve 7 can be either a manual pressure regulating valve or an electric pressure regulating valve. When an electric pressure regulating valve is selected, it needs to be connected to the output port of the controller, and the power cord needs to be connected to the power port of the controller (the specifics are existing technology and will not be elaborated here).
[0036] In some alternative embodiments, the compressor exhaust pipe 12 is sealed to the heat sink pipe 9 by threads, the end of the heat sink pipe 9 away from the compressor exhaust pipe 12 is sealed to the first flow meter 5 by a flange joint, and the end of the first flow meter 5 away from the heat sink pipe 9 is sealed to the reversing pipe 6 by a flange joint.
[0037] Specifically, an external thread is made on the compressor exhaust pipe 12, and an internal thread is made on the end of the heat dissipation pipe 9, so as to realize the threaded connection between the two; the sealing connection through the flange joint refers to the two components that need to be connected being fixed with flanges (by welding or integral molding, etc.), the two flanges being connected by bolts, and a rubber gasket being sandwiched between the two flanges.
[0038] In some alternative embodiments, a three-way valve is sealed between the reversing line 6 and the turbine intake line 10 via a flange joint. The third port of the three-way valve is sealed to the pressure regulating valve 7 via a flange joint, and the end of the pressure regulating valve 7 away from the three-way valve is sealed to the muffler 8.
[0039] The first port of the three-way valve is sealed to the reversing pipe 6 through a flange joint, the second port is sealed to the turbine intake pipe 10 through a flange joint, the third port is sealed to the pressure regulating valve 7 through a flange joint, and the pressure regulating valve 7 is sealed to the silencer 8 through a flange joint.
[0040] In some alternative embodiments, the turbine expander exhaust line is sealed to the second flow meter 11 via a flange joint.
[0041] The first flow meter 5 and the second flow meter 11 can respectively monitor the exhaust flow of the centrifugal compressor 2 and the exhaust flow of the turbine expander 3.
[0042] In some alternative embodiments, an air filter 13 is fixedly connected to the stand 4. The exhaust end of the air filter 13 is sealed to the compressor intake pipe 1 through a hose and a clamp. The end of the compressor intake pipe 1 away from the air filter 13 is sealed to the intake end of the centrifugal compressor 2 through a hose and a clamp.
[0043] The connection is sealed using a hose and a clamp, which involves placing the hose over the pipe to be connected and locking it with a clamp. A rubber gasket can be placed between the hose and the pipe.
[0044] In some alternative embodiments, several heat dissipation fins are fixed to the outer wall of the heat dissipation pipe 9. This results in a large surface area, which can be used as a preliminary cooler to initially cool the high-temperature gas discharged from the centrifugal compressor 2.
[0045] In some alternative embodiments, a number of casters 15 are fixed to the bottom of the stand 4 to facilitate movement of the device.
[0046] The working principle of this invention is as follows: During operation, the centrifugal compressor 2 rotates at high speed. Clean air filtered by the air filter 13 is drawn into the centrifugal compressor 2 through the compressor intake pipe 1. The air at normal temperature and pressure becomes high temperature and high pressure air and then enters the compressor exhaust pipe 12. It is initially cooled by the heat dissipation pipe 9, and then enters the turbine expander 3 through the reversing pipe 6 and the turbine intake pipe 10. Utilizing the principle of expansion refrigeration, the high temperature and high pressure gas becomes low temperature and low pressure gas. The turbine expander 3 generates cooling energy to the outside environment while rotating at high speed. During this process, the intake pressure and temperature of the centrifugal compressor 2, the exhaust pressure and temperature of the centrifugal compressor 2, the intake pressure and temperature of the turbine expander 3, and the exhaust pressure and temperature of the turbine expander 3 can be measured. This testing system can perform tests in different combinations by replacing the centrifugal compressor 2 and the turbine expander 3. By changing the speed of the centrifugal compressor 2 and the opening of the pressure regulating valve 7, the system's variable operating condition performance test can be achieved.
[0047] In the description of this utility model, it should be understood that the terms "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.
[0048] The embodiments described above are merely preferred embodiments of the present utility model and are not intended to limit the scope of the present utility model. Various modifications and improvements made to the technical solutions of the present utility model by those skilled in the art without departing from the spirit of the present utility model should fall within the protection scope defined by the claims of the present utility model.
Claims
1. A testing system for a fully dynamic pressure air refrigeration system, characterized in that: Includes a stand (4), on which a centrifugal compressor (2) and a turbo expander (3) are detachably connected. The exhaust end of the centrifugal compressor (2) and the inlet end of the turbo expander (3) are connected through a first connecting pipe. A pressure regulating valve (7) is provided on the first connecting pipe. The inlet end of the centrifugal compressor (2) is detachably connected to a compressor inlet pipe (1), and the exhaust end of the turbo expander (3) is detachably connected to a turbo expander exhaust pipe. A first pressure detection element and a first temperature detection element are provided on the compressor intake pipe (1) and on the first connecting pipe near the exhaust end of the centrifugal compressor (2). A second pressure detection element and a second temperature detection element are provided on the turbine expander exhaust pipe and on the first connecting pipe near the intake end of the turbine expander (3). The pressure regulating valve (7) is located between the first pressure detection element at the exhaust end of the centrifugal compressor (2) and the second pressure detection element at the intake end of the turbine expander (3).
2. The test system for a fully dynamic pressure air refrigeration system according to claim 1, characterized in that: The first connecting pipeline includes a compressor exhaust pipeline (12), a heat dissipation pipe (9), a reversing pipeline (6), and a turbine intake pipeline (10) connected in sequence. The exhaust end of the centrifugal compressor (2) is sealed to the compressor exhaust pipeline (12) through a hose and a clamp. The turbine intake pipeline (10) is sealed to the intake end of the turbine expander (3) through a flange joint. The pressure regulating valve (7) is located between the reversing pipeline (6) and the turbine intake pipeline (10). The first pressure detection element and the first temperature detection element of the exhaust end of the centrifugal compressor (2) are installed on the compressor exhaust pipeline (12). The second pressure detection element and the second temperature detection element of the intake end of the turbine expander (3) are installed on the turbine intake pipeline (10).
3. The test system for a fully dynamic pressure air refrigeration system according to claim 2, characterized in that: The compressor exhaust pipe (12) is sealed to the heat dissipation pipe (9) by a thread. The end of the heat dissipation pipe (9) away from the compressor exhaust pipe (12) is sealed to the first flow meter (5) by a flange joint. The end of the first flow meter (5) away from the heat dissipation pipe (9) is sealed to the reversing pipe (6) by a flange joint.
4. The test system for a fully dynamic pressure air refrigeration system according to claim 2, characterized in that: A three-way valve is sealed between the reversing pipeline (6) and the turbine intake pipeline (10) through a flange joint. The third port of the three-way valve is sealed to the pressure regulating valve (7) through a flange joint. The end of the pressure regulating valve (7) away from the three-way valve is sealed to the silencer (8).
5. The test system for a fully dynamic pressure air refrigeration system according to claim 2, characterized in that: The turbine expander exhaust pipe is sealed to the second flow meter (11) via a flange joint.
6. The test system for a fully dynamic pressure air refrigeration system according to claim 1, characterized in that: An air filter (13) is fixedly connected to the stand (4). The exhaust end of the air filter (13) is sealed to the compressor intake pipe (1) through a hose and a clamp. The end of the compressor intake pipe (1) away from the air filter (13) is sealed to the intake end of the centrifugal compressor (2) through a hose and a clamp.
7. The test system for a fully dynamic pressure air refrigeration system according to claim 2, characterized in that: Several heat dissipation fins are fixed to the outer wall of the heat dissipation pipe (9).
8. The test system for a fully dynamic pressure air refrigeration system according to claim 1, characterized in that: The bottom of the platform (4) is fixed with several casters (15).