CN110793802B - Double-closed indirect cooling compressor experiment system - Google Patents
Double-closed indirect cooling compressor experiment system Download PDFInfo
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- CN110793802B CN110793802B CN201911187908.7A CN201911187908A CN110793802B CN 110793802 B CN110793802 B CN 110793802B CN 201911187908 A CN201911187908 A CN 201911187908A CN 110793802 B CN110793802 B CN 110793802B
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Abstract
The invention discloses a double-closed type indirect cold compressor experiment system which comprises two tested compressors, a rectification and voltage stabilization unit, an air charging and discharging unit, a surge experiment unit and the like. The experimental system has the experimental capacity of a single-stage compressor or a double-stage indirect cooling compressor, is suitable for performance experiments of stable medium compressors such as air, carbon dioxide and nitrogen, and effectively expands the test range of the test bed; the experimental system can meet the requirements of the indirect cooling compressor on air inlet parameters, particularly the requirement of high inlet pressure, so that the flow state of the indirect cooling compressor is truly simulated, and the internal flow-heat transfer coupling mechanism of the indirect cooling compressor is revealed; the experimental system has surge experimental capacity, can carry out the research on the stalling and surge mechanism of the compressor, and has the experimental capacity from normal pressure to high pressure.
Description
Technical Field
The invention belongs to the technical field related to compressor testing, and relates to a compressor experiment system, in particular to a double-closed type indirect cold compressor experiment system.
Background
At present, compressed air energy storage has the advantages of no geographic condition limitation, high energy storage efficiency, environmental friendliness, capability of recovering waste heat and the like, is considered to be a large-scale physical energy storage technology with the most development potential, and has wide market prospect. The characteristics of the compressed air energy storage system are combined, a centrifugal or axial flow type is usually adopted for the air compressor, and the pneumatic and mechanical performance experiments and detection of the compressor are necessary to be carried out to know the internal flow and heat transfer coupling rule, so that the requirements of the compressed air energy storage system on high efficiency and wide working conditions are met, and the key scientific problem in the air energy storage compression system is solved.
According to different experimental types, the experimental system of the compressor can be divided into an open type and a closed type, but the traditional experimental system of the compressor only aims at a single-section or inter-section air extraction compressor set and cannot meet the experimental requirements of the indirect compressor for the compressed air energy storage system, particularly the research requirements of the flow-heat transfer coupling mechanism of the indirect compressor with high air inlet and exhaust pressure.
Disclosure of Invention
The invention aims to provide an experimental system of a double-closed indirect cold compressor, which aims to solve the problems in the background art, has the experimental capability of a single-stage compressor or a double-stage indirect cold compressor, is suitable for performance experiments of various stable medium compressors, and effectively expands the test range of a test bed; the experimental system can also meet the requirements of the indirect cooling compressor on air inlet parameters, particularly high inlet pressure requirements, so that the flow state of the indirect cooling compressor is truly simulated, and the internal flow-heat transfer coupling mechanism of the indirect cooling compressor is revealed; the experimental system also has surge experimental capacity, can carry out the research on the stalling and surge mechanism of the compressor, and has the experimental capacity from normal pressure to high pressure.
In order to achieve the purpose, the invention adopts the following technical scheme:
a double-closed type intercooling compressor experiment system comprises a first tested compressor, a second tested compressor and a pressure stabilizing tank, and is characterized in that,
the pressure stabilizing tank is provided with a first pressure stabilizing inlet, a second pressure stabilizing inlet, a first pressure stabilizing outlet and a second pressure stabilizing outlet, wherein,
the first pressure stabilizing outlet and the second pressure stabilizing outlet are respectively communicated with the air inlets of the first tested compressor and the second tested compressor after passing through at least a stop valve, a pressure stabilizing valve group, a flowmeter and a rectifying device in sequence through pipelines;
the communication pipelines between the air inlets of the first and second tested compressors and the first and second pressure stabilizing outlets are respectively formed into air inlet pipelines of the first and second tested compressors;
the exhaust ports of the first tested compressor and the second tested compressor are communicated with the first pressure stabilizing inlet and the second pressure stabilizing inlet respectively through pipelines at least sequentially passing through a check valve, a heat exchanger and a stop valve;
the communication pipelines between the exhaust ports of the first and second tested compressors and the first and second pressure stabilizing inlets are respectively formed into exhaust pipelines of the first and second tested compressors;
a surge communication pipeline with an anti-surge valve group is arranged between the inlet of the check valve on the exhaust pipeline of each tested compressor and the inlet of the rectifying device on the air inlet pipeline of the tested compressor;
a communicating pipeline with a stop valve is arranged between the outlet of the heat exchanger on the exhaust pipeline of each tested compressor and the outlet of the pressure stabilizing valve group on the air inlet pipeline of the other tested compressor, and the communicating pipeline is formed into a linkage communicating pipeline of the two tested compressors;
the pressure stabilizing tank, the pressure stabilizing valve group and the rectifying device are arranged on the air inlet pipeline of each tested compressor to form a rectifying and pressure stabilizing unit of the experimental system, so that the inlet pressure and the flow field quality of the tested compressors can meet the experimental requirements;
still set up an air supplement pipeline and an air bleed pipeline on the surge tank, air supplement pipeline and air bleed pipeline all with the surge tank intercommunication, just be equipped with the tonifying qi governing valve on the air supplement pipeline, be equipped with the air bleed governing valve on the air bleed pipeline, the surge tank with air supplement pipeline and air bleed pipeline form into the inflation and deflation unit of experiment system.
The double-closed type indirect cold compressor experiment system has the experiment capacity of a single-stage compressor or a double-stage indirect cold compressor, is suitable for performance experiments of stable medium compressors such as air, carbon dioxide, nitrogen and the like, and can effectively expand the test range of the experiment system; the experimental system can meet the requirements of the indirect cooling compressor on air inlet parameters, particularly the requirement of high inlet pressure, so that the flow state of the indirect cooling compressor is truly simulated, and the internal flow-heat transfer coupling mechanism of the indirect cooling compressor is revealed; in the experimental system, the air inlet temperature of the tested compressor is adjusted through the heat exchanger, and the air inlet pressure and flow of the tested compressor are adjusted through the pressure stabilizing valve bank, so that the experimental test of the compressor is realized; the rectification and voltage stabilization unit ensures that the inlet pressure and the flow field quality of the tested compressor meet the experimental requirements.
As a preferable scheme of the present invention, the experimental system further includes a variable frequency speed control driving unit, and the variable frequency speed control driving unit is configured to drive the first tested compressor and the second tested compressor.
Furthermore, the variable-frequency speed regulation driving unit comprises a double-shaft extension motor and two speed-increasing gear boxes, wherein the double-shaft extension motor is provided with a frequency converter, two output shafts of the double-shaft extension motor are respectively connected with the input shafts of the two speed-increasing gear boxes through a clutch, and each output shaft of the speed-increasing gear box is respectively provided with a torque detector and is respectively in driving connection with the first and second tested compressors. The variable-frequency speed regulation driving unit regulates the rotating speed of the motor through the frequency converter and utilizes the speed-up gear box to reach the rotating speed required by the compressor; the two speed-up gear boxes are utilized to reach the rotating speeds required by the first and second tested compressors, and the output torque of the speed-up gear boxes is measured through the torque measuring device; the double-shaft extension motor can drive the two speed-up gear boxes simultaneously, and power switching is carried out by utilizing the clutch.
Furthermore, the speed increasing gear box is provided with a plurality of output shafts, so that different speed increasing ratios can be switched, and different experimental rotating speeds of the compressors can be met.
In a preferred embodiment of the present invention, the first and second compressors to be tested are a single-stage axial compressor, a multistage axial compressor, a single-stage centrifugal compressor, or a multistage centrifugal compressor.
As a preferable scheme of the invention, a plurality of filter elements are arranged in the pressure stabilizing tank and used for removing redundant water in the experiment process and ensuring the drying of the medium.
As a preferable scheme of the present invention, the pressure stabilizing valve group has a valve position feedback function, and at least includes a main pressure stabilizing valve and an auxiliary pressure stabilizing valve.
As a preferable scheme of the invention, the rectifying device adopts a rectifying grid to reduce the whirling of the air flow entering the tested compressor.
In a preferred embodiment of the present invention, each of the stop valves is a manual stop valve or an electric stop valve.
As a preferable scheme of the invention, each anti-surge valve group comprises a main anti-surge valve and an auxiliary anti-surge valve.
In a preferred embodiment of the present invention, each check valve is a through-flow check valve to reduce pressure loss in the pipeline.
As a preferable scheme of the invention, each heat exchanger is a high-efficiency tube-fin heat exchanger, adopts fins to increase the heat exchange area, and is provided with a wire mesh water removal device.
As a preferable scheme of the invention, each flowmeter is a porous balanced flowmeter, the length of the front and rear straight pipe sections is shortened, and the occupied area is reduced.
As a preferable scheme of the present invention, the experimental system at least includes a single-tested-compressor experimental test mode, a double-tested-compressor linkage experimental test mode, and a surge experimental test mode.
Further, when the experimental system is in a single-tested-compressor experimental test mode, one of the two tested compressors is started, and the other is closed; for the started compressor to be tested, opening each stop valve on the air inlet pipeline and the exhaust pipeline of the compressor to be tested; for the un-started tested compressor, closing each stop valve on the air inlet pipeline and the exhaust pipeline of the compressor; and closing the stop valves on the linkage communication pipelines.
Further, when the experimental system is in a double-tested-compressor linkage experimental test mode, the two tested compressors are started simultaneously, and for one tested compressor, stop valves on an air inlet pipeline and an exhaust pipeline of the tested compressor are opened; and for the other tested compressor, opening the stop valve on the air inlet pipeline, closing the stop valve on the exhaust pipeline and opening the stop valve on the corresponding linkage communication pipeline.
Furthermore, the exhaust ports of the first and second tested compressors are respectively provided with a pressure sensor, and each anti-surge valve bank is in a normally closed state; when the experiment system is in a surge experiment test mode, monitoring the exhaust pressure value of the first tested compressor or the second tested compressor, if the exhaust pressure value of one tested compressor is monitored to have small fluctuation, increasing the opening degree of an auxiliary anti-surge valve on a surge communication pipeline of the tested compressor, and performing surge approximation after the surge is properly relieved, so that a surge experiment is completed; if the exhaust pressure value of a certain tested compressor is monitored to have large fluctuation, a main anti-surge valve on a surge communication pipeline of the tested compressor is quickly opened, and the surge is quickly relieved.
As a preferred scheme of the invention, the experimental system further comprises a charge-discharge air regulation mode, the air inlets of the first and second tested compressors are both provided with a pressure sensor, and in the experimental process, if the monitored air inlet pressure value of one tested compressor is smaller than the experimental required value, the opening degree of the air supply regulating valve is increased; and if the monitored air inlet pressure value of a certain tested compressor is greater than the experimental required value, increasing the opening degree of the air bleeding regulating valve.
Compared with the prior art, the invention has the beneficial effects that:
(1) the double-closed type indirect cold compressor experiment system provided by the invention has the experiment capacity of a single-stage compressor or a double-stage indirect cold compressor, is suitable for performance experiments of stable medium compressors such as air, carbon dioxide, nitrogen and the like, and effectively expands the test range of a test bed;
(2) the double-closed type indirect cooling compressor experiment system provided by the invention can meet the requirements of indirect cooling compressors on air inlet parameters, particularly high inlet pressure requirements, so that the flow state of the indirect cooling compressors is truly simulated, and the internal flow-heat transfer coupling mechanism of the indirect cooling compressors is revealed;
(3) the double-closed type intercooling compressor experiment system provided by the invention has surge experiment capacity, can be used for carrying out compressor stall and surge mechanism research, and has the experiment capacity from normal pressure to high pressure.
Drawings
Fig. 1 is a schematic diagram of an experimental system of a double closed type indirect cooling compressor of the present invention.
Fig. 2 is a schematic diagram of the first tested compressor during experimental tests.
Fig. 3 is a schematic view of the second tested compressor during experimental tests.
FIG. 4 is a schematic diagram of the test carried out by the linkage experiment of the load compressors 9-23.
FIG. 5 is a schematic diagram of the test carried out by the load cell 23-9 linkage experiment.
FIG. 6 is a schematic diagram of the experimental system during a charge/discharge regulation and surge experiment.
The same reference numbers will be used throughout the drawings to refer to the same or like elements or structures, wherein:
1-frequency converter, 2-motor, 3/6-clutch, 4/7-speed-increasing gear box, 5/8-torque measuring device, 9-first measured compressor, 10/22-rectifying device, 11/21-flowmeter, 12/19-main pressure stabilizing valve, 13/20 auxiliary pressure stabilizing valve, 14/18/25/26/28/29-stop valve, 15-pressure stabilizing tank, 16-air supply regulating valve, 17-air discharge regulating valve, 23-second measured compressor, 24/32-check valve, 27/33-heat exchanger, 30/35-main anti-surge valve and 31/34-auxiliary anti-surge valve.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is further described in detail below with reference to the accompanying drawings and examples.
As shown in fig. 1, the experimental system of the double-closed indirect cooling compressor of the invention comprises a frequency converter 1, a motor 2, a clutch 3/6, a speed-increasing gear box 4/7, a torque measuring device 5/8, a first measured compressor 9, a rectifying device 10/22, a flow meter 11/21, a main pressure stabilizing valve 12/19, an auxiliary pressure stabilizing valve 13/20, a stop valve 14/18/25/26/28/29, a pressure stabilizing tank 15, an air supply adjusting valve 16, an air discharge adjusting valve 17, a second measured compressor 23, a check valve 24/32, a heat exchanger 27/33, a main anti-surge valve 30/35, an auxiliary anti-surge valve 31/34, pipelines and valve groups.
Specifically, the first measured compressor 9 and the second measured compressor 23 may be a single-stage axial compressor, a multistage axial compressor, a single-stage centrifugal compressor, or a multistage centrifugal compressor. The first load-to-be-tested compressor 9 and the second load-to-be-tested compressor 23 are driven by a variable frequency variable speed drive unit. The variable frequency speed regulation driving unit comprises a double-shaft extension motor 2 and two speed-increasing gear boxes 4 and 7, wherein the double-shaft extension motor 2 is provided with a frequency converter 1, the rotating speed of the double-shaft extension motor 2 is regulated through the frequency converter 1, two output shafts of the double-shaft extension motor 2 are respectively connected with input shafts of the two speed-increasing gear boxes 4 and 7 through clutches 3 and 6, each output shaft of each speed-increasing gear box 4 and 7 is respectively provided with a torque measuring device 5 and 8 and is respectively in driving connection with a first pressure-measured compressor 9 and a second pressure-measured compressor 23, the required rotating speeds of the first pressure-measured compressor 9 and the second pressure-measured compressor 23 are achieved by utilizing the two speed-increasing gear boxes 4 and 7, and the output torques of the speed-increasing gear boxes 4 and 7 are measured through the torque measuring devices 5 and 8.
The pressure stabilizing tank 15 is provided with a first pressure stabilizing inlet, a second pressure stabilizing inlet, a first pressure stabilizing outlet and a second pressure stabilizing outlet, wherein the first pressure stabilizing outlet and the second pressure stabilizing outlet are respectively communicated with the air inlets of the first compressor 9 and the second compressor 23 to be tested after passing through at least a stop valve 14/18, a pressure stabilizing valve group, a flowmeter 11/21 and a rectifying device 10/22 in sequence through pipelines; the communication lines between the air inlets of the first and second compressors under test 9, 23 and the first and second steady pressure outlets are formed as air inlet lines of the first and second compressors under test 9, 23, respectively. The exhaust ports of the first tested compressor 9 and the second tested compressor 23 respectively at least sequentially pass through a check valve 24/32, a heat exchanger 27/33 and a stop valve 26/28 through pipelines and then are communicated with the first pressure-stabilizing inlet and the second pressure-stabilizing inlet; the communication pipelines between the exhaust ports of the first and second tested compressors 9 and 23 and the first and second pressure-stabilizing inlets are respectively formed as exhaust pipelines of the first and second tested compressors 9 and 23; a check valve 24/32 on the exhaust line of each tested compressor 9, 23, a surge communication line with an anti-surge valve group is arranged between the inlet of the check valve 24/32 and the inlet of the rectifying device 10/22 on the air inlet line of the tested compressor 9, 23; a communicating pipeline with a stop valve 25/29 is arranged between the outlet of the heat exchanger 27/33 on the exhaust pipeline of each tested compressor 9, 23 and the outlet of the pressure stabilizing valve group on the air inlet pipeline of the other tested compressor 23, 9, and the communicating pipeline is formed into a linkage communicating pipeline of double tested compressors; the pressure stabilizing tank 15 is further provided with an air supplementing pipeline and an air discharging pipeline, the air supplementing pipeline and the air discharging pipeline are communicated with the pressure stabilizing tank 15, an air supplementing regulating valve 16 is arranged on the air supplementing pipeline, an air discharging regulating valve 17 is arranged on the air discharging pipeline, and the pressure stabilizing tank 15, the air supplementing pipeline and the air discharging pipeline form an air charging and discharging unit of the experimental system.
The surge tank 15, and the surge valve group and the rectifying device 10/22 arranged on the air inlet pipeline of each tested compressor 9, 23 form a rectifying and pressure stabilizing unit of the experimental system, so as to ensure that the inlet pressure and the flow field quality of the tested compressor meet the experimental requirements. A plurality of filter elements are arranged in the pressure stabilizing tank 15 and used for removing redundant water in the experimental process and ensuring the drying of the medium. Each pressure stabilizing valve group has a valve position feedback function and at least comprises a main pressure stabilizing valve 12/19 and an auxiliary pressure stabilizing valve 13/20. A flow straightener 10/22 is provided to reduce turbulence in the air flow entering the compressor being tested. Each stop valve is a manual stop valve or an electric stop valve.
An anti-surge valve block provided between the intake and exhaust lines of each of the tested compressors 9, 23 and a check valve 24/32 provided on the exhaust line, formed as a surge test unit of the test system, is implemented by introducing the tested compressor outlet air flow into the intake. Each anti-surge valve bank includes a main anti-surge valve 30/35 and an auxiliary anti-surge valve 31/34. Each check valve 24/32 is a through-flow check valve to reduce line pressure losses.
The double-closed type indirect cold compressor experiment system at least comprises a single-tested compressor experiment test mode, a double-tested compressor linkage experiment test mode, a surge experiment test mode and other various test modes and charging and discharging regulation modes.
Example 1
Fig. 2 shows the situation when the first tested compressor 9 is in the experimental test mode. As shown in fig. 2, when the experimental system performs an experimental test on the first tested compressor 9, the first tested compressor 9 is started, the second tested compressor 23 is closed, the stop valves on the air inlet pipeline and the air exhaust pipeline of the second tested compressor 23 and the stop valves 18, 25, 28 and 29 on the linkage communication pipelines need to be closed, and the stop valves 14 and 26 on the air inlet pipeline and the air exhaust pipeline of the first tested compressor 9 are opened. The gas flows into the first tested compressor 9 through the flow meter 11 to be pressurized, then the temperature is reduced through the heat exchanger 33, then the gas flows into the pressure stabilizing tank 15 to reduce the gas flow pulsation, finally the gas is reduced in pressure through the main pressure stabilizing valve 12 and the auxiliary pressure stabilizing valve 13 and then enters the first tested compressor 9 again, and the closed cycle is completed. In the experiment process, the opening degrees of the main pressure maintaining valve 12 and the auxiliary pressure maintaining valve 13 are adjusted, so that the experiment requirements of the first tested compressor 9 under different flow working conditions are met.
Example 2
Fig. 3 shows the second tested compressor 23 in the experimental test mode. Referring to fig. 3, when the experimental system performs an experimental test on the second tested compressor 23, it is necessary to close the stop valves on the air inlet pipeline and the exhaust pipeline of the first tested compressor 9 and the stop valves 14, 25, 26, and 29 on the linkage communication pipelines, and open the stop valves 18 and 28 on the air inlet pipeline and the exhaust pipeline of the second tested compressor 23. The gas flows into the second tested compressor 23 through the flow meter 21 to be pressurized, then the temperature is reduced through the heat exchanger 27, then the gas flows into the pressure stabilizing tank 15 to reduce the gas flow pulsation, finally the gas is reduced in pressure through the main pressure stabilizing valve 19 and the auxiliary pressure stabilizing valve 20 and then enters the second tested compressor 23 again, and the closed cycle is completed. In the experiment process, the opening degrees of the main pressure maintaining valve 19 and the auxiliary pressure maintaining valve 20 are adjusted, so that the experiment requirements of the second tested compressor 23 under different flow working conditions are met.
Example 3
Fig. 4 shows the situation when tested by the test of the compressor 9-23 linkage. Referring to fig. 4, when the experimental system is used for carrying out the test of the linkage experiment of the compressor 9-23, the stop valves 18, 26 and 29 need to be closed, and the stop valves 14, 25 and 28 need to be opened. The gas flows into the first tested compressor 9 through the flow meter 11 to be pressurized, then the temperature is reduced through the heat exchanger 33, then the gas flows into the second tested compressor 23 to be further pressurized, the temperature is reduced through the heat exchanger 27, finally the airflow pulsation is reduced in the pressure stabilizing tank 15, the pressure is reduced through the main pressure stabilizing valve 12 and the auxiliary pressure stabilizing valve 13, and then the gas reenters the first tested compressor 9 to complete the closed cycle. In the experiment process, the opening degrees of the main pressure stabilizing valve 12 and the auxiliary pressure stabilizing valve 13 are adjusted, so that the experiment requirements of the first and second tested compressors 9 and 23 under different flow working conditions are met.
Example 4
Fig. 5 shows the situation when tested by the load compressor 23-9 linkage experiment. Referring to fig. 5, the experimental system is used for carrying out the test of the linked experiment of the tested compressor 23-9, and the stop valves 14, 25 and 28 are closed and the stop valves 18, 26 and 29 are opened. The gas flows into the second tested compressor 23 through the flow meter 21 to be pressurized, then the temperature is reduced through the heat exchanger 27, then the gas flows into the first tested compressor 9 to be further pressurized, the temperature is reduced through the heat exchanger 33, finally the airflow pulsation is reduced in the pressure stabilizing tank 15, the pressure is reduced through the main pressure stabilizing valve 19 and the auxiliary pressure stabilizing valve 20, and then the gas reenters the tested compressor 23, and the closed cycle is completed. In the experiment process, the experiment requirements of the pressure-measured compressors 23 and 9 under different flow working conditions are met by adjusting the main pressure maintaining valve 19 and the auxiliary pressure maintaining valve by 20 degrees.
Example 5
Fig. 6 shows a surge experiment and a state when the experiment system performs the charge/discharge control. As shown in fig. 6, the experimental system increases the opening degree of the gas compensation regulating valve 16 by monitoring the intake pressure of the first tested compressor 9 or the second tested compressor 23 according to different test experimental requirements, if the intake pressure is smaller than an experimental required value; if the inlet pressure is greater than the experimentally required value, the opening degree of the bleed air adjustment valve 17 is increased.
When the experimental system performs a surge experiment, the exhaust pressure of the first tested compressor 9 or the second tested compressor 23 is monitored, if the exhaust pressure fluctuates slightly, the opening degree of the auxiliary anti-surge valve 31 or 34 can be increased, and after the surge is properly relieved, the surge is forced, so that the surge experiment is completed; if the exhaust pressure has large fluctuation, the main anti-surge valve 30 or 35 is rapidly opened, and the surge is rapidly relieved.
In conclusion, the double-closed type indirect cold compressor experiment system provided by the invention has the experiment capacity of a single-stage compressor or a double-stage indirect cold compressor, is suitable for performance experiments of stable medium compressors such as air, carbon dioxide and nitrogen, and effectively expands the test range of a test bed; the experimental system provided by the invention can meet the requirements of the indirect cooling compressor on air inlet parameters, particularly the requirement of high inlet pressure, so that the flow state of the indirect cooling compressor is truly simulated, and the internal flow-heat transfer coupling mechanism is revealed; the experimental system provided by the invention has surge experimental capability, can be used for researching the stalling and surge mechanisms of the compressor, and has the experimental capability from normal pressure to high pressure.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (17)
1. A double-closed type intercooling compressor experiment system comprises a first tested compressor, a second tested compressor and a pressure stabilizing tank, and is characterized in that,
the pressure stabilizing tank is provided with a first pressure stabilizing inlet, a second pressure stabilizing inlet, a first pressure stabilizing outlet and a second pressure stabilizing outlet, wherein,
the first pressure stabilizing outlet and the second pressure stabilizing outlet are respectively communicated with the air inlets of the first tested compressor and the second tested compressor after passing through at least a stop valve, a pressure stabilizing valve group, a flowmeter and a rectifying device in sequence through pipelines;
the communication pipelines between the air inlets of the first and second tested compressors and the first and second pressure stabilizing outlets are respectively formed into air inlet pipelines of the first and second tested compressors;
the exhaust ports of the first tested compressor and the second tested compressor are communicated with the first pressure stabilizing inlet and the second pressure stabilizing inlet respectively through pipelines at least sequentially passing through a check valve, a heat exchanger and a stop valve;
the communication pipelines between the exhaust ports of the first and second tested compressors and the first and second pressure stabilizing inlets are respectively formed into exhaust pipelines of the first and second tested compressors;
a surge communication pipeline with an anti-surge valve group is arranged between the inlet of the check valve on the exhaust pipeline of each tested compressor and the inlet of the rectifying device on the air inlet pipeline of the tested compressor;
a communicating pipeline with a stop valve is arranged between the outlet of the heat exchanger on the exhaust pipeline of each tested compressor and the outlet of the pressure stabilizing valve group on the air inlet pipeline of the other tested compressor, and the communicating pipeline is formed into a linkage communicating pipeline of the two tested compressors;
the pressure stabilizing tank, the pressure stabilizing valve group and the rectifying device are arranged on the air inlet pipeline of each tested compressor to form a rectifying and pressure stabilizing unit of the experimental system, so that the inlet pressure and the flow field quality of the tested compressors can meet the experimental requirements;
the pressure stabilizing tank is also provided with an air supplementing pipeline and an air discharging pipeline, the air supplementing pipeline and the air discharging pipeline are both communicated with the pressure stabilizing tank, an air supplementing regulating valve is arranged on the air supplementing pipeline, an air discharging regulating valve is arranged on the air discharging pipeline, and the pressure stabilizing tank, the air supplementing pipeline and the air discharging pipeline form an air discharging unit of the experimental system;
each stop valve is a manual stop valve or an electric stop valve.
2. The dual close refrigeration compressor test system of claim 1, further comprising a VFSG drive unit configured to drive the first and second tested compressors.
3. The experimental system of a double-closed type indirect cold compressor as claimed in claim 2, wherein the variable-frequency speed-regulating driving unit comprises a double-shaft extension motor and two speed-increasing gear boxes, wherein the double-shaft extension motor is provided with a frequency converter, two output shafts of the double-shaft extension motor are respectively connected with input shafts of the two speed-increasing gear boxes through a clutch, and output shafts of each speed-increasing gear box are respectively provided with a torque detector and are respectively connected with the first and second tested compressors in a driving way; the variable-frequency speed regulation driving unit regulates the rotating speed of the motor through the frequency converter and utilizes the speed-up gear box to reach the rotating speed required by the compressor; the two speed-up gear boxes are utilized to reach the rotating speeds required by the first and second tested compressors, and the output torque of the speed-up gear boxes is measured through the torque measuring device; the double-shaft extension motor can drive the two speed-up gear boxes simultaneously, and power switching is carried out by utilizing the clutch.
4. The dual closed type intermediate cold compressor experiment system as claimed in claim 3, wherein the speed increasing gear box is provided with a plurality of output shafts, so that different speed increasing ratios can be switched to meet different experimental rotating speeds of the compressor.
5. A dual close-shut cold compressor pilot system according to claim 1, wherein said first and second tested compressors are single stage axial compressors, multistage axial compressors, single stage centrifugal compressors or multistage centrifugal compressors.
6. The experimental system of a double-closed type indirect cold compressor as claimed in claim 1, wherein a plurality of filter elements are arranged in the pressure stabilizing tank and used for removing excessive moisture in the experimental process and ensuring the drying of the medium.
7. The experimental system of a double-closing type indirect cold compressor as claimed in claim 1, wherein the pressure stabilizing valve group has a valve position feedback function and at least comprises a main pressure stabilizing valve and an auxiliary pressure stabilizing valve.
8. The dual close indirect cold compressor test system of claim 1, wherein the flow straightener is a flow straightener to reduce turbulence of the air flow entering the compressor being tested.
9. The dual close refrigeration compressor testing system of claim 1, wherein each said anti-surge valve bank comprises a main anti-surge valve and an auxiliary anti-surge valve.
10. The dual close refrigeration compressor testing system of claim 1, wherein each of said check valves is a through-flow check valve to reduce line pressure losses.
11. The dual-enclosure cold compressor experimental system according to claim 1, wherein each of said heat exchanger types is a high efficiency tube and fin heat exchanger, uses fins to increase heat exchange area, and is provided with wire mesh water removal devices.
12. The experimental system of a double-closed indirect cold compressor as claimed in claim 1, wherein each of the flow meters is a multi-hole balanced flow meter, the length of the front and rear straight pipe sections is shortened, and the floor space is reduced.
13. The dual close indirect cold compressor test system of claim 1, wherein the test system comprises at least a single load compressor test mode, a dual load compressor ganged test mode, and a surge test mode.
14. The dual close indirect cold compressor test system of claim 13, wherein when the test system is in a single-load-compressor test mode, one of the two load compressors is on and the other is off; for the started compressor to be tested, opening each stop valve on the air inlet pipeline and the exhaust pipeline of the compressor to be tested; for the un-started tested compressor, closing each stop valve on the air inlet pipeline and the exhaust pipeline of the compressor; and closing the stop valves on the linkage communication pipelines.
15. The dual close type inter-cold compressor experiment system according to claim 13, wherein when the experiment system is in a dual-load-compressor linkage experiment test mode, two load compressors are simultaneously started, and for one of the load compressors, each stop valve on an air inlet pipeline and an air outlet pipeline of the load compressor is opened; and for the other tested compressor, opening the stop valve on the air inlet pipeline, closing the stop valve on the exhaust pipeline and opening the stop valve on the corresponding linkage communication pipeline.
16. The dual close type intercooled cold compressor experimental system of claim 13, wherein the exhaust ports of the first and second compressors to be tested are provided with pressure sensors, and each of the anti-surge valve banks is in a normally closed state; when the experiment system is in a surge experiment test mode, monitoring the exhaust pressure value of the first tested compressor or the second tested compressor, if the exhaust pressure value of one tested compressor is monitored to have small fluctuation, increasing the opening degree of an auxiliary anti-surge valve on a surge communication pipeline of the tested compressor, and performing surge approximation after the surge is properly relieved, so that a surge experiment is completed; if the exhaust pressure value of a certain tested compressor is monitored to have large fluctuation, a main anti-surge valve on a surge communication pipeline of the tested compressor is quickly opened, and the surge is quickly relieved.
17. The experimental system of a double-closed indirect cold compressor as claimed in claim 1, further comprising a charging and discharging air adjusting mode, wherein the air inlets of the first and second tested compressors are respectively provided with a pressure sensor, and in the experimental process, if the value of the intake pressure of one tested compressor is monitored to be smaller than the experimental requirement value, the opening degree of the gas-supplementing adjusting valve is increased; and if the monitored air inlet pressure value of a certain tested compressor is greater than the experimental required value, increasing the opening degree of the air bleeding regulating valve.
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| CN2722218Y (en) * | 2004-06-01 | 2005-08-31 | 浙江大学 | Performance testing table of air conditioner compressor on vehicle |
| CN101649831B (en) * | 2009-09-04 | 2011-07-20 | 合肥通用机械研究院 | Performance testing device of carbon dioxide refrigeration compressor for refrigeration systems |
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| CN205823603U (en) * | 2016-07-21 | 2016-12-21 | 九江天赐高新材料有限公司 | The testing device of hydrogen gas compressor |
| CN106121993B (en) * | 2016-08-18 | 2017-08-01 | 江苏雪梅制冷设备有限公司 | The performance testing device of CO2 refrigeration compressors and its complete unit |
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