CN108343600B - Performance test board for compressor and use method - Google Patents
Performance test board for compressor and use method Download PDFInfo
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- CN108343600B CN108343600B CN201810308164.9A CN201810308164A CN108343600B CN 108343600 B CN108343600 B CN 108343600B CN 201810308164 A CN201810308164 A CN 201810308164A CN 108343600 B CN108343600 B CN 108343600B
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- 238000011056 performance test Methods 0.000 title claims abstract description 14
- 238000000034 method Methods 0.000 title claims description 19
- 239000007788 liquid Substances 0.000 claims abstract description 73
- 238000001704 evaporation Methods 0.000 claims abstract description 32
- 230000008020 evaporation Effects 0.000 claims abstract description 32
- 230000001105 regulatory effect Effects 0.000 claims abstract description 29
- 238000012360 testing method Methods 0.000 claims abstract description 27
- 238000001035 drying Methods 0.000 claims abstract description 18
- 239000000110 cooling liquid Substances 0.000 claims description 60
- 239000003507 refrigerant Substances 0.000 claims description 39
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 28
- 238000001816 cooling Methods 0.000 claims description 21
- 230000001276 controlling effect Effects 0.000 claims description 10
- 238000007639 printing Methods 0.000 claims description 4
- 238000005086 pumping Methods 0.000 claims description 3
- 239000003921 oil Substances 0.000 description 66
- 239000002826 coolant Substances 0.000 description 12
- 239000013526 supercooled liquid Substances 0.000 description 7
- 238000006073 displacement reaction Methods 0.000 description 4
- 238000005057 refrigeration Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 239000000243 solution Substances 0.000 description 3
- 239000003795 chemical substances by application Substances 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000002474 experimental method Methods 0.000 description 2
- 238000007710 freezing Methods 0.000 description 2
- 230000008014 freezing Effects 0.000 description 2
- 239000010726 refrigerant oil Substances 0.000 description 2
- 230000029058 respiratory gaseous exchange Effects 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 239000012809 cooling fluid Substances 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000005485 electric heating Methods 0.000 description 1
- 230000006698 induction Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B51/00—Testing machines, pumps, or pumping installations
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Testing Resistance To Weather, Investigating Materials By Mechanical Methods (AREA)
- Compressor (AREA)
Abstract
The invention discloses a performance test bench for a compressor, which comprises a rack, wherein an exhaust pipe, an oil separator, a calorimeter, a gas-liquid separator and an air suction pipe which are sequentially connected are arranged on the rack, the exhaust pipe is connected with an exhaust port of the compressor, the air suction pipe is connected with an air suction port of the compressor, a condenser, a drying filter and an evaporation condenser which are sequentially connected are also arranged on the rack, an air outlet end of the calorimeter is connected with a second connecting pipe, the condenser is positioned on the second connecting pipe, a liquid outlet end of the second connecting pipe is connected with a liquid inlet end of the drying filter, a regulating valve is arranged on the second connecting pipe, a liquid outlet end of the drying filter is connected with a liquid inlet end of the evaporation condenser, an electronic expansion valve is arranged between the drying filter and the evaporation condenser, and an air outlet end of the evaporation condenser is connected with an air inlet end of the gas-liquid separator. The invention can make a test bench suitable for compressors of various types without frequently replacing the condenser, so that the test bench has higher applicability and reduces the cost of single use.
Description
Technical Field
The invention relates to a compressor, in particular to a performance test bench for a compressor and a use method.
Background
Compared with the common compressors, the positive displacement enthalpy-increasing compressor (such as a screw compressor, an air injection enthalpy-increasing scroll compressor and the like) has the advantages of high energy efficiency, wide temperature range and high reliability, and is widely and widely applied. Therefore, the research and improvement of the refrigeration performance of the compressor are of great significance. However, the conventional test of the refrigerating capacity has certain defects, so that the refrigerating capacity test deviation of the positive displacement enthalpy-increasing compressor is large, and the high-efficiency development of the compressor is not conveniently guided.
The performance test method of the GB/T5773-2004 positive displacement refrigerant compressor can obtain that the refrigerating capacity test device for the positive displacement enthalpy-increasing compressor with the refrigerating capacity below 75KW is shown in figure 1. There are two methods for calculating the refrigerating capacity, namely an X method and a Y method, and the two methods are simultaneously measured, so that the deviation of the result is within 4%. The X method is a second refrigerant calorimeter method, and the Y method is a refrigerant liquid flow meter method. The refrigerating capacity calculating method is as follows:
x method: phi X = phi i + F (ta-ts) hg2-hf2vgavg1 (hg 1-hf 1) - - - (1)
And (3) a Y method: phi Y=qm2 vgavg1 (hg 1-hf 1) - - - (2)
In the formula (1), phi is the electric heating power of a calorimeter and is measured by a test bed calorimeter power meter; f (ta-ts) is the heat leakage quantity and is calculated according to the temperature difference inside and outside the calorimeter; hg2 is the actual specific enthalpy of the refrigerant leaving the calorimeter; hf2 is the actual specific enthalpy of the liquid refrigerant entering the expansion valve 101; hg1 is the theoretical specific enthalpy of inspiration under the specified working condition; hf1 is the theoretical specific enthalpy of the refrigerant entering the expansion valve 101 under the specified operating conditions. In the formula (2), vga is the actual specific volume of inspiration; vg1 is the theoretical specific volume of inspiration under the specified working condition.
In actual operation, the suction superheat degree of the compressor needs to be controlled, so that the influence on the operation of the compressor due to the fact that the suction superheat degree is too high or too low is avoided, and further, larger errors are caused in experimental results. The condensing effect of the condenser is generally controlled to control the suction superheat degree, namely, if different compressors need to be tested or different working conditions need to be tested, the condenser needs to be replaced. The invention improves the experimental cost and also makes the applicability of the test equipment single.
Disclosure of Invention
Aiming at the defects of the prior art, the invention aims to provide a performance test bench for a compressor.
In order to achieve the above purpose, the present invention provides the following technical solutions:
the utility model provides a performance test bench for compressor, includes the frame, install blast pipe, oil separator, calorimeter, gas-liquid separator and the breathing pipe that link to each other in order in the frame, the blast pipe links to each other with the gas vent of compressor, the breathing pipe links to each other with the induction port of compressor, still install condenser, dry filter and the evaporation condenser that link to each other in order in the frame, the end of giving vent to anger of calorimeter is connected with the second connecting pipe, the condenser is located the second connecting pipe, the play liquid end of second connecting pipe links to each other with dry filter's inlet end, keep away from dry filter one end on the second connecting pipe and be equipped with the governing valve that is used for controlling second connecting pipe aperture, dry filter's play liquid end links to each other with evaporation condenser's inlet end, be equipped with electronic expansion valve between dry filter and the evaporation condenser, evaporation condenser's the end of giving vent to anger and gas-liquid separator's inlet end are connected.
By adopting the technical scheme, the refrigerant enters the condenser after passing through the calorimeter, exchanges heat with the cooling liquid in the condenser, is condensed into high-pressure liquid, then passes through the dry filter, throttles the liquid into low-pressure gas-liquid two-phase fluid through the electronic expansion valve, enters the evaporation condenser, then enters the air suction port of the compressor, and is compressed and discharged through the compressor to complete the refrigerant circulation.
The suction superheat degree can be controlled according to specific test working conditions and specific tested compressors, and the suction pressure and the exhaust pressure are both in the set working condition range. The invention can make a test bench suitable for compressors of various types without frequently replacing the condenser, so that the test bench has higher applicability and reduces the cost of single use.
The invention is further provided with: the second connecting pipe is connected with the liquid inlet end of the evaporation condenser, and the liquid outlet end of the evaporation condenser is connected with the liquid inlet end of the drying filter.
By adopting the technical scheme, the high-temperature and high-pressure refrigerant gas discharged by the compressor is subjected to primary condensation by absorbing heat by water in the condenser, and then enters the evaporative condenser. The other side of the evaporative condenser is the liquid refrigerant in the liquid reservoir, which is throttled by the electronic expansion valve into the refrigerant of low-temperature low-pressure two-phase fluid. The refrigerant in two different states exchanges heat in the evaporative condenser, wherein the refrigerant with low temperature and low pressure absorbs heat and then becomes superheated gas, and the superheated gas is sucked by the compressor; the refrigerant which is primarily condensed in the condenser is continuously condensed into supercooled liquid in the evaporation condenser, enters the evaporation condenser after being throttled by the electronic expansion valve, continuously condenses the refrigerant which is primarily condensed in the condenser, becomes superheated gas and is sucked by the compressor.
The air suction pressure is regulated by an electronic expansion valve, the air suction temperature is regulated by the heat exchange capacity of the condenser, the heat exchange capacity of the condenser is regulated by the water inlet temperature and the water flow, and the condensing pressure is regulated by a front regulating valve of the condenser.
The invention is further provided with: one side of the second connecting pipe is connected with a third connecting pipe, the third connecting pipe is connected with the liquid inlet end of the evaporation condenser, and the liquid outlet end of the evaporation condenser is connected with the liquid inlet end of the drying filter.
By adopting the technical scheme, one part of high-temperature and high-pressure refrigerant gas exhausted by the compressor enters the condenser to be condensed, the other part of high-temperature and high-pressure refrigerant gas enters the evaporation condenser to be condensed, the condensed refrigerant gas becomes supercooled liquid, the supercooled liquid enters the evaporation condenser after being throttled by the electronic expansion valve, and the supercooled liquid becomes superheated gas to be sucked by the compressor after absorbing heat in the evaporation condenser. Wherein the suction pressure is regulated by an electronic expansion valve; the air suction temperature is regulated by the heat exchange capacity of the condenser and a front regulating valve of the condenser; the heat exchange capacity of the condenser is regulated by the water inlet temperature and water flow; the condensing pressure is regulated by an electric valve in front of the condenser.
The invention is further provided with: a fourth connecting pipe is connected between the dry filter and the condenser, a liquid reservoir is connected to the fourth connecting pipe, and the liquid reservoir is positioned between the dry filter and the condenser.
Through adopting above-mentioned technical scheme, the cistern can play a cushioning effect, makes drying filter's drying rate and the speed that the condensing agent flowed through the condenser each other not influence, can not lead to the inadequately of drying because the condensing agent flowed through the speed of condenser is too fast to the appearance that has reduced the stifled phenomenon of ice has improved the precision of test.
The invention is further provided with: the vacuum pump is arranged on the frame, exhaust pipes and air suction pipes are connected with the vacuum pump, pressure controllers are arranged on the exhaust pipes and the air suction pipes, exhaust valves for controlling the opening and the closing of the exhaust pipes are arranged on the exhaust pipes, and air suction valves for controlling the opening and the closing of the air suction pipes are arranged on the air suction pipes.
Through adopting above-mentioned technical scheme, before the test, firstly take out the air in the compressor through the vacuum pump, and then reduce the vapor in the air and condense the phenomenon that blocks up expansion valve or pipeline formation ice and stop up under low temperature, make the experiment can go on more smoothly.
The invention is further provided with: the oil outlet end of the oil separator is connected with an oil cooler, the oil outlet end of the oil cooler is connected with an oil supply pipe, one end, opposite to the oil cooler, of the oil supply pipe is connected into the compressor, and an oil supply valve is arranged on the oil supply pipe.
Through adopting above-mentioned technical scheme, the frozen oil that separates from the oil separator carries out heat exchange with the coolant liquid in the oil cooler through the oil cooler, reduces the frozen oil temperature to the required temperature, flows into the compressor, lubricates, seals yin and yang rotor and moving part to make the operation that the compressor can be more stable.
The invention is further provided with: the cooling device comprises a cooling tower, wherein a cooling liquid inlet pipe is connected between a cooling liquid inlet end of an oil cooler, a cooling liquid inlet end of a calorimeter and a cooling liquid inlet end of a condenser and the cooling tower, a water pump is arranged on the cooling liquid inlet pipe, a cooling liquid outlet pipe is connected between a cooling liquid outlet end of the oil cooler, a cooling liquid outlet end of the calorimeter and the cooling liquid outlet end of the condenser and the cooling tower, a three-way valve is arranged on the cooling liquid outlet pipe, and the three-way valve is connected with the cooling liquid inlet pipe.
Through adopting above-mentioned technical scheme, come the aperture of control coolant liquid drain pipe through the three-way valve, under the same circumstances of water pump supply pressure, the aperture of coolant liquid drain pipe changes, can change the radiating flow of coolant liquid through the cooling tower, and then has changed the water temperature of intaking of heat exchanger, further control heat exchange ability of heat exchanger.
The invention further aims to provide a using method of the performance test board, which can stably and accurately test the refrigerating capacity and the refrigerating coefficient of the compressor.
In order to achieve the above purpose, the present invention provides the following technical solutions:
a method of using the performance test bench as claimed in claim 7, comprising the steps of,
s1, connecting an exhaust pipe to an exhaust port of a compressor, connecting an air suction pipe to an air suction port of the compressor, and connecting an oil supply pipe to an oil supply port of the compressor;
s2, connecting a high-pressure measuring point and an exhaust temperature measuring point to a high-pressure connecting pipeline of the tested compressor, connecting a low-pressure connecting pipeline of the tested compressor to a low-pressure measuring point and an exhaust temperature measuring point, and pumping out air in the compressor through a vacuum pump;
s3, sequentially opening an exhaust valve, an air suction valve and an oil supply valve;
s4, enabling the regulating valve to reach a specified opening degree;
s5, starting the water pump and the compressor to be compressed, and gradually opening a loading electromagnetic valve on the compressor to be compressed;
s6, observing whether the suction pressure and the exhaust pressure reach the set working condition range, and if necessary, adjusting the regulating valve to enable the suction pressure and the exhaust pressure to reach the set working condition range;
s7, opening an electromagnetic expansion valve or a manual expansion valve to adjust the air suction temperature, adjusting the adjustment valve, the electromagnetic expansion valve or the manual expansion valve in a linkage way at the moment, setting data acquisition time after the working condition is stabilized, clicking an acquisition button on test software, clicking a print test report button after acquisition is finished, and storing and printing test data;
s8, gradually closing a loading electromagnetic valve on the compressor to be compressed, then closing an air suction valve, closing the compressor to be compressed when the air suction pressure is reduced to negative pressure, and closing a water pump, an air discharge valve and an oil supply valve;
s9, detaching the compressor from the frame.
By adopting the technical scheme, the refrigerating capacity of the compressor can be calculated according to the calculation method in GB/T5773-2004 by the experimental data tested by the steps. The refrigeration coefficient is obtained from the refrigeration capacity and the input power of the compressor (measured by a power meter).
The invention is further provided with: when all the equipment is closed after the test is finished, the water pump is operated for more than three minutes, so that the pipeline is ensured to be cooled.
By adopting the technical scheme, each pipeline is prevented from being still in a high-temperature state after the equipment is closed, the possibility of cracking of the pipeline due to high-temperature aging is reduced, and the service life of the pipeline is prolonged.
The invention has the following advantages: 1. the air suction superheat degree of the compressor can be adjusted under the adjustment of using the same condenser, so that the test error is reduced; 2. the test bench can test compressors of various types; 3. the test bench can stably operate; 4. energy saving.
Drawings
FIG. 1 is a schematic diagram of a prior art compressor refrigeration capacity testing apparatus;
FIG. 2 is a schematic diagram of the structure of the first embodiment;
fig. 3 is a schematic structural diagram of a second embodiment.
Reference numerals: 1. a frame; 2. an exhaust pipe; 3. an oil separator; 4. a calorimeter; 5. a condenser; 6. drying the filter; 7. an evaporative condenser; 8. an air suction pipe; 9. a vacuum pump; 10. an exhaust pipe; 11. a pressure controller; 12. an exhaust valve; 13. an air suction valve; 14. a first connection pipe; 15. an oil cooler; 16. an oil supply pipe; 17. an oil supply valve; 18. a water storage tank; 19. a cooling liquid inlet pipe; 20. a water pump; 21. a cooling liquid outlet pipe; 22. a three-way valve; 23. a second connection pipe; 24. a regulating valve; 25. a fourth connection pipe; 26. a liquid reservoir; 27. an electronic expansion valve; 28. a compressor; 29. a gas-liquid separator; 30. and a third connection pipe.
Detailed Description
The invention is further described with reference to the accompanying drawings.
Embodiment one:
as shown in fig. 2, a performance test stand for a compressor includes a frame 1, and an exhaust pipe 2, an oil separator 3, a calorimeter 4, a condenser 5, a dry filter 6, an evaporation condenser 7, a gas-liquid separator 29, and an air suction pipe 8 are sequentially installed on the frame 1. The frame 1 is provided with a vacuum pump 9, and an exhaust pipe 10 is connected between the exhaust pipe 2 and the air suction pipe 8 and between the exhaust pipe and the vacuum pump 9. The exhaust pipe 2 and the air suction pipe 8 are both provided with a pressure controller 11, the exhaust pipe 2 is provided with an exhaust valve 12 for controlling the opening and closing of the exhaust pipe 2, and the air suction pipe 8 is provided with an air suction valve 13 for controlling the opening and closing of the air suction pipe 8.
The exhaust pipe 2 is connected with an exhaust port of the compressor 28, one end of the exhaust pipe 2 is connected with a liquid inlet end of the oil separator 3, and a liquid outlet end of the oil separator 3 is connected with a first connecting pipe 14. The refrigerant enters the oil separator 3 from the discharge pipe 2 and exits the oil separator 3 through the first connecting pipe 14. The oil outlet end of the oil separator 3 is connected with an oil cooler 15, the oil outlet end of the oil cooler 15 is connected with an oil supply pipe 16, one end of the oil supply pipe 16 opposite to the oil cooler 15 is connected into a compressor 28, and the oil supply pipe 16 is provided with an oil supply valve 17. When the refrigerant passes through the oil separator 3, the oil separator 3 may separate the refrigerant from the refrigerant pool, and this part of the refrigerant passes through the oil cooler 15, exchanges heat with the coolant in the oil cooler 15, reduces the temperature of the refrigerant to a desired temperature, and flows into the compressor 28, thereby lubricating and sealing the male and female rotors and the moving parts.
The frame 1 is provided with a (water storage tank) 18 for supplying cooling fluid to the oil cooler 15. A coolant inlet pipe 19 is connected between the coolant inlet end of the oil cooler 15 and the cooling tower 18. A water pump 20 is arranged on the cooling liquid inlet pipe 19. A coolant outlet pipe 21 is connected between the coolant outlet end of the oil cooler 15 and the cooling tower 18. The cooling liquid outlet pipe 21 is provided with a three-way valve 22, and the three-way valve 22 is connected with the cooling liquid inlet pipe 19. The cooling liquid has two flow lines according to the opening degree of the three-way valve 22, namely, the liquid fed from the cooling liquid feed pipe 19 passes through the oil cooler 15 to exchange heat with the frozen oil, and then directly flows back to the cooling tower 18 from the cooling liquid discharge pipe 21; secondly, after the liquid fed from the cooling liquid feed pipe 19 passes through the oil cooler 15 and exchanges heat with the freezing oil, the liquid flows into the cooling liquid outlet pipe 21 and flows back to the cooling liquid feed pipe 19 again, and the liquid exchanges heat with the freezing oil again. And further controls the degree of cooling of the cooling oil by the oil cooler 15.
The end of the first connecting pipe 14, which is far away from the oil separator 3, is connected with the air inlet end of the calorimeter 4. The air outlet end of the calorimeter 4 is connected with a second connecting pipe 23. The refrigerant enters the calorimeter 4 from the first connection pipe 14 and leaves the calorimeter 4 through the second connection pipe 23.
A cooling liquid inlet pipe 19 is connected between the cooling liquid inlet end of the calorimeter 4 and the cooling tower 18. A water pump 20 is arranged on the cooling liquid inlet pipe 19. A cooling liquid outlet pipe 21 is connected between the cooling liquid outlet end of the calorimeter 4 and the cooling tower 18. The cooling liquid outlet pipe 21 is provided with a three-way valve 22, and the three-way valve 22 is connected with the cooling liquid inlet pipe 19. The cooling liquid has two flow lines according to the opening of the three-way valve 22, namely, the liquid enters from the cooling liquid inlet pipe 19, passes through the calorimeter 4 to exchange heat with the calorimeter 4, and then directly flows back to the cooling tower 18 from the cooling liquid outlet pipe 21; secondly, after the liquid fed from the cooling liquid feed pipe 19 passes through the calorimeter 4 to exchange heat with the calorimeter 4, the liquid flows into the cooling liquid outlet pipe 21 and flows back to the cooling liquid feed pipe 19 again to exchange heat with the calorimeter 4 again. And further controls the heat exchange capacity of the calorimeter 4, so that the temperature of the inlet liquid and the temperature difference of the inlet liquid and the outlet liquid of the cooling liquid reach the specified requirements.
The second connecting pipe 23 is provided with a regulating valve 24, and the regulating valve 24 can be used for controlling the opening degree of the second connecting pipe 23. The condenser 5 is mounted on the second connection pipe 23. After heat exchange by the calorimeter 4, the refrigerant flows into the condenser 5 through the second connecting pipe 23, exchanges heat with the cooling liquid, and then flows out of the condenser 5. The discharge pressure of the compressor can be regulated by controlling the regulating valve 24, so that the discharge pressure of the compressor is stabilized at the discharge pressure required by the experiment.
A coolant inlet pipe 19 is connected between the coolant inlet end of the condenser 5 and the cooling tower 18. A water pump 20 is arranged on the cooling liquid inlet pipe 19. A cooling liquid outlet pipe 21 is connected between the cooling liquid outlet end of the condenser 5 and the cooling tower 18. The cooling liquid outlet pipe 21 is provided with a three-way valve 22, and the three-way valve 22 is connected with the cooling liquid inlet pipe 19. The cooling liquid has two flow lines according to the opening of the three-way valve 22, namely, the liquid enters from the cooling liquid inlet pipe 19, passes through the condenser 5 to exchange heat with the refrigerant, and then directly flows back to the cooling tower 18 from the cooling liquid outlet pipe 21; secondly, the liquid fed from the cooling liquid feeding pipe 19 flows into the cooling liquid outlet pipe 21 after heat exchange with the refrigerant through the condenser 5, and flows back to the cooling liquid feeding pipe 19 again to perform heat exchange with the refrigerant again. And further controls the degree of cooling of the refrigerant oil by the condenser 5.
The second connecting pipe 23 is connected with the liquid inlet end of the evaporative condenser 7, and the liquid outlet end of the evaporative condenser 7 is connected with the fourth connecting pipe 25. The fourth connecting pipe 25 is connected with the liquid inlet end of the dry filter 6. The fourth connecting pipe 25 is connected to a liquid reservoir 26. The liquid outlet end of the dry filter 6 is connected with the liquid inlet end of the evaporative condenser 7, and an electronic expansion valve 27 is arranged between the dry filter 6 and the evaporative condenser 7. The outlet end of the evaporative condenser 7 is connected to the inlet end of the gas-liquid separator 29. The gas outlet end of the gas-liquid separator 29 is connected with the gas suction pipe 8. The suction pipe 8 is connected to a suction port of the compressor 28.
The working principle of the performance test bench is as follows:
the high-pressure gas discharged from the compressor 28 first enters the oil separator 3 to separate the refrigerant oil from the refrigerant, and then the high-temperature high-pressure refrigerant gas discharged from the compressor 28 is primarily condensed by the heat absorbed by the water in the condenser 5, and enters the evaporative condenser 5. The liquid refrigerant in the liquid receiver 26 is throttled by the electronic expansion valve 27 to a low-temperature low-pressure two-phase fluid refrigerant on the other side of the evaporative condenser 5. The refrigerant in two different states exchanges heat in the evaporative condenser 5, wherein the refrigerant with low temperature and low pressure absorbs heat and becomes superheated gas, which is sucked by the compressor 28; the refrigerant initially condensed in the condenser 5 is continuously condensed into a supercooled liquid in the evaporator-condenser 5, and after being throttled by the electronic expansion valve 27, enters the evaporator-condenser 5, and is continuously condensed into a superheated gas which is sucked by the compressor 28 in the condenser 5, thereby completing the cycle.
The refrigerating oil separated from the oil separator 3 passes through the oil cooler 15, exchanges heat with the coolant in the oil cooler 15, lowers the temperature of the refrigerating oil to a desired temperature, and flows into the compressor 28 to lubricate and seal the male and female rotors and the moving parts.
Embodiment two:
the difference between the second embodiment and the first embodiment is that:
as shown in fig. 3, the second connection pipe 23 is directly connected to the liquid inlet end of the dry filter 6. A third connecting pipe 30 is connected to one side of the second connecting pipe 23, the third connecting pipe 30 is connected to the liquid inlet end of the evaporation condenser 5, and the liquid outlet end of the evaporation condenser 5 is connected to the liquid inlet end of the fourth connecting pipe 25.
Part of the high-temperature and high-pressure refrigerant gas discharged from the compressor 28 enters the condenser 5 to be condensed, the other part enters the evaporation condenser 5 to be condensed, the condensed refrigerant gas becomes supercooled liquid, the supercooled liquid enters the evaporation condenser 5 after being throttled by the electronic expansion valve 27, and the superheated gas is sucked by the compressor 28 after absorbing heat in the evaporation condenser 5 to complete the cycle. Wherein the suction pressure is regulated by an electronic expansion valve 27; the suction temperature is regulated by the heat exchange capacity of the condenser 5 and the regulating valve 24 in front of the condenser 5; the heat exchange capacity of the condenser 5 is regulated by the water inlet temperature and water flow; the condensing pressure is regulated by an electrically operated valve in front of the condenser 5.
Embodiment III:
s1, connecting an exhaust pipe 2 to an exhaust port of a compressor 28, connecting an air suction pipe 8 to an air suction port of the compressor 28, and connecting an oil supply pipe 16 to an oil supply port of the compressor 28;
s2, connecting a high-pressure measuring point and an exhaust temperature measuring point to a high-pressure connecting pipeline of the tested compressor 28, connecting a low-pressure connecting pipeline of the tested compressor 28 to a low-pressure measuring point and an exhaust temperature measuring point, and pumping out air in the compressor 28 through a vacuum pump 9;
s3, sequentially opening the exhaust valve 12, the suction valve 13 and the oil supply valve 17;
s4, enabling the regulating valve 24 to reach a specified opening degree;
s5, starting the water pump 20 and the compressor 28 to be compressed, and gradually opening a loading electromagnetic valve on the compressor 28 to be compressed;
s6, observing whether the suction pressure and the exhaust pressure reach the set working condition range, and if necessary, adjusting the regulating valve 24 to enable the suction pressure and the exhaust pressure to reach the set working condition range;
s7, opening the electronic expansion valve 27 or the manual expansion valve to adjust the air suction temperature, adjusting the adjusting valve 24, the electronic expansion valve 27 or the manual expansion valve in a linkage way at the moment, setting data acquisition time after the working condition is stabilized, clicking an acquisition button on test software, clicking a print test report button after acquisition is finished, and storing and printing test data;
s8, gradually closing a loading electromagnetic valve on the compressor 28 to be tested, then closing the suction valve 13, closing the compressor 28 to be tested when the suction pressure is reduced to negative pressure, and closing the water pump 20, the exhaust valve 12 and the oil supply valve 17; when all the equipment is closed after the test is finished, the water pump 20 is operated for more than three minutes, so that the pipeline is ensured to be cooled;
s9, the compressor 28 is detached from the frame 1.
The above description is only a preferred embodiment of the present invention, and the protection scope of the present invention is not limited to the above examples, and all technical solutions belonging to the concept of the present invention belong to the protection scope of the present invention. It should be noted that modifications and adaptations to the present invention can be made by one of ordinary skill in the art without departing from the principles of the present invention and are intended to be within the scope of the present invention.
Claims (2)
1. A performance test bench for a compressor comprises a frame (1), and is characterized in that: the air conditioner is characterized in that an exhaust pipe (2), an oil separator (3), a calorimeter (4), a gas-liquid separator (29) and an air suction pipe (8) which are sequentially connected are arranged on the frame (1), the exhaust pipe (2) is connected with an air outlet of a compressor (28), the air suction pipe (8) is connected with an air suction inlet of the compressor (28), a condenser (5), a drying filter (6) and an evaporation condenser (7) which are sequentially connected are also arranged on the frame (1), the air outlet end of the calorimeter (4) is connected with a second connecting pipe (23), the condenser (5) is positioned on the second connecting pipe (23), the liquid outlet end of the second connecting pipe (23) is connected with the liquid inlet end of the drying filter (6), one end, far away from the drying filter (6), of the second connecting pipe (23) is provided with a regulating valve (24) for controlling the opening degree of the second connecting pipe, the liquid inlet end of the drying filter (6) is connected with the liquid outlet end of the evaporation condenser (7), an electronic expansion valve (7) is arranged between the drying filter (6) and the air outlet end of the evaporation condenser (7), and the air inlet end of the evaporator (29) is connected with the air inlet end of the air outlet end of the evaporator (29).
The liquid outlet end of the drying filter (6) is connected with the liquid inlet end at the lower side of the evaporation condenser (7);
the high-temperature and high-pressure refrigerant gas discharged by the compressor (28) is primarily condensed in the condenser (5) by absorbing heat by water, and enters the evaporation condenser (7);
the second connecting pipe (23) is connected with the liquid inlet end of the upper side of the evaporation condenser (7) after passing through the condenser (5), and the liquid outlet end of the lower side of the evaporation condenser (7) is connected with the liquid inlet end of the drying filter (6);
a liquid outlet end at the lower side of the evaporation condenser (7) is connected with a fourth connecting pipe (25), a liquid reservoir (26) is connected to the fourth connecting pipe (25), and the liquid reservoir (26) is positioned between the drying filter (6) and the condenser (5);
the vacuum pump (9) is arranged on the frame (1), an exhaust pipe (10) is connected between the exhaust pipe (2) and the air suction pipe (8) and the vacuum pump (9), pressure controllers (11) are arranged on the exhaust pipe (2) and the air suction pipe (8), an exhaust valve (12) for controlling the opening and closing of the exhaust pipe (2) is arranged on the exhaust pipe (2), and an air suction valve (13) for controlling the opening and closing of the air suction pipe (8) is arranged on the air suction pipe (8);
the oil outlet end of the oil separator (3) is connected with an oil cooler (15), the oil outlet end of the oil cooler (15) is connected with an oil supply pipe (16), one end, opposite to the oil cooler (15), of the oil supply pipe (16) is connected into a compressor (28), and an oil supply valve (17) is arranged on the oil supply pipe (16);
the cooling device comprises a cooling tower, wherein a cooling liquid inlet pipe (19) is connected between a cooling liquid inlet end of an oil cooler (15), a cooling liquid inlet end of a calorimeter (4) and a cooling liquid inlet end of a condenser (5) and the cooling tower, a water pump (20) is arranged on the cooling liquid inlet pipe (19), a cooling liquid outlet pipe (21) is connected between a cooling liquid outlet end of the oil cooler (15), a cooling liquid outlet end of the calorimeter (4) and a cooling liquid outlet end of the condenser (5) and the cooling tower, a three-way valve (22) is arranged on the cooling liquid outlet pipe (21), and the three-way valve (22) is connected with the cooling liquid inlet pipe (19);
the performance test bench comprises the following using steps,
s1, connecting an exhaust pipe (2) to an exhaust port of a compressor (28), connecting an air suction pipe (8) to an air suction port of the compressor (28), and connecting an oil supply pipe (16) to an oil supply port of the compressor (28);
s2, connecting a high-pressure measuring point and an exhaust temperature measuring point to a high-pressure connecting pipeline of the tested compressor (28), connecting a low-pressure connecting pipeline of the tested compressor (28) to the low-pressure measuring point and the exhaust temperature measuring point, and pumping out air in the compressor (28) through a vacuum pump (9);
s3, sequentially opening an exhaust valve (12), an air suction valve (13) and an oil supply valve (17);
s4, enabling the regulating valve (24) to reach a specified opening degree;
s5, starting the water pump (20) and the compressor (28) to be compressed, and gradually opening a loading electromagnetic valve on the compressor (28) to be compressed;
s6, observing whether the suction pressure and the exhaust pressure reach the set working condition range, and if necessary, adjusting the regulating valve (24) to enable the suction pressure and the exhaust pressure to reach the set working condition range;
s7, opening an electronic expansion valve (27) to adjust the air suction temperature, adjusting a regulating valve (24) and the electronic expansion valve (27) in a linkage way at the moment, setting data acquisition time after a working condition is stabilized, clicking an acquisition button on test software, clicking a printing test report button after acquisition is finished, and storing and printing test data;
s8, gradually closing a loading electromagnetic valve on the compressor (28) to be compressed, then closing an air suction valve (13), closing the compressor (28) to be compressed when the air suction pressure is reduced to negative pressure, and closing a water pump (20), an exhaust valve (12) and an oil supply valve (17);
s9, detaching the compressor (28) from the frame (1).
2. A method of using the performance test bench of claim 1, wherein: the use method is characterized in that the use step is as claimed in claim 1, and then when all the devices are closed at the end of the test, the water pump (20) is operated for more than three minutes to ensure that the pipeline is cooled.
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| CN109882400B (en) * | 2019-03-29 | 2020-07-07 | 四川虹美智能科技有限公司 | Testing device of compressor |
| CN110454375A (en) * | 2019-07-08 | 2019-11-15 | 合肥通用机械研究院有限公司 | Use nitrogen as the system of refrigerant detection compressor effect |
| CN110529377A (en) * | 2019-10-09 | 2019-12-03 | 江苏中关村科技产业园节能环保研究有限公司 | Compressor reliability test macro |
| CN111059043A (en) * | 2019-12-23 | 2020-04-24 | 王佳元 | Novel roots vacuum pump test system |
| CN112267997B (en) * | 2020-11-26 | 2021-06-25 | 中家院（北京）检测认证有限公司 | Compressor performance testing system and method |
| CN114414274A (en) * | 2021-12-28 | 2022-04-29 | 势加透博(重庆)科技有限公司 | Measurement and control system of closed refrigeration cycle test device |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20010028942A (en) * | 1999-09-28 | 2001-04-06 | 김평길 | Performance tester of two-stage centrifugal compressor |
| CN102338075A (en) * | 2011-10-15 | 2012-02-01 | 合肥天鹅制冷科技有限公司 | Performance test device and test method for refrigeration compressor |
| CN204389071U (en) * | 2015-01-23 | 2015-06-10 | 珠海格力节能环保制冷技术研究中心有限公司 | Positive displacement increases enthalpy compressor refrigerating capacity proving installation |
| CN208184948U (en) * | 2018-04-08 | 2018-12-04 | 浙江商业机械厂有限公司 | It is a kind of for the performance test bed of compressor |
-
2018
- 2018-04-08 CN CN201810308164.9A patent/CN108343600B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20010028942A (en) * | 1999-09-28 | 2001-04-06 | 김평길 | Performance tester of two-stage centrifugal compressor |
| CN102338075A (en) * | 2011-10-15 | 2012-02-01 | 合肥天鹅制冷科技有限公司 | Performance test device and test method for refrigeration compressor |
| CN204389071U (en) * | 2015-01-23 | 2015-06-10 | 珠海格力节能环保制冷技术研究中心有限公司 | Positive displacement increases enthalpy compressor refrigerating capacity proving installation |
| CN208184948U (en) * | 2018-04-08 | 2018-12-04 | 浙江商业机械厂有限公司 | It is a kind of for the performance test bed of compressor |
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