CN117249077A - Performance test device for double-suction double-row compressor - Google Patents
Performance test device for double-suction double-row compressor Download PDFInfo
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- CN117249077A CN117249077A CN202311039212.6A CN202311039212A CN117249077A CN 117249077 A CN117249077 A CN 117249077A CN 202311039212 A CN202311039212 A CN 202311039212A CN 117249077 A CN117249077 A CN 117249077A
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- 238000011056 performance test Methods 0.000 title claims description 18
- 230000001105 regulatory effect Effects 0.000 claims abstract description 194
- 239000003507 refrigerant Substances 0.000 claims abstract description 173
- 238000012360 testing method Methods 0.000 claims abstract description 76
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 18
- 238000000034 method Methods 0.000 description 32
- 230000001276 controlling effect Effects 0.000 description 11
- 238000010586 diagram Methods 0.000 description 8
- 238000010438 heat treatment Methods 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 3
- 238000013461 design Methods 0.000 description 2
- 238000005485 electric heating Methods 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000030279 gene silencing Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
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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
Abstract
The invention discloses a performance testing device for a double-suction double-row compressor, which comprises a first refrigerant loop, a first oil return path, a second refrigerant loop and a second oil return path, wherein various parameters of the loop are independently controlled through a condenser, a subcooler, an oil separator, a calorimeter and a plurality of regulating valves, so that the performance of the double-suction double-row compressor and the accuracy and the authenticity of endurance test data are ensured.
Description
Technical Field
The invention particularly relates to a performance testing device for a double-suction double-row compressor.
Background
At present, most indoor units of air conditioners adopt a double-row heat exchanger structure, and when air flows through a first row of heat exchangers, the temperature of the air changes, so that the temperature difference between the air and a second row of heat exchangers is reduced, and the heat exchange performance is possibly reduced. Particularly, under the dehumidifying working condition of the air conditioner, the electric auxiliary heat is added to control the ring temperature in a proper range, so that the energy consumption is reduced. Aiming at the situation, a plurality of compressors and air conditioner manufacturers start to develop double-suction double-row compressors, the evaporating temperature and the condensing temperature are controlled in a double-way mode, and the evaporating temperature and the condensing temperature of the double-row heat exchanger can be differentially controlled according to working conditions.
The interfaces of the double-suction double-row compressor are shown in fig. 1, the compressor is provided with two exhaust ports, two air suction ports are arranged, the system refrigerant enters from the first air suction port and exits from the first air suction port, a first refrigerant loop can be formed, the system refrigerant enters from the second air suction port and exits from the second air suction port, a second refrigerant loop can be formed, when the operation working conditions are different, the suction pressure, the exhaust pressure, the suction temperature and the pre-valve temperature of the two refrigerant loops are different, the refrigerant flow is also different, and the two refrigerant loops are enabled to realize different refrigerating capacity or heating capacity corresponding to different working conditions.
Corresponding to the structural characteristics and application scenes of the double-suction double-row compressor, the performance of the test compressor needs to be controlled respectively for the suction and exhaust of the double-suction ports and the double-discharge ports of the compressor, and the performance and durability test equipment of the existing compressor are designed for the single-suction single-discharge compressor with one suction port and one exhaust port and cannot be used for performance test of the double-suction double-discharge compressor.
In addition, there are a single suction double row compressor as shown in fig. 2 and a double suction single row compressor as shown in fig. 3, where the single suction double row compressor has a first suction port, a first exhaust port and a second exhaust port, which can form a refrigerant circuit of the first suction port and the second exhaust port, the exhaust pressures of the two exhaust ports are different, the suction pressure and the suction temperature are the same under the same working condition, and the refrigerant flows of the two exhaust ports are different. The double suction single-row compressor has two suction ports, namely a first suction port and a second suction port, and a first discharge port, which can form a refrigerant circuit, and the suction pressures or suction temperatures of the two suction ports can be different. Therefore, the single-suction double-row compressor and the double-suction single-row compressor cannot adopt the existing test equipment to perform performance and durability tests.
Disclosure of Invention
The invention aims to provide a performance testing device for a double-suction double-row compressor, which aims to accurately test the performance and durability of the double-suction double-row compressor.
The technical scheme of the invention is as follows:
a performance testing device for a double suction double row compressor, comprising:
a first refrigerant circuit: one end of the first refrigerant flow meter is connected with an air outlet I of the compressor, and the other end of the first refrigerant flow meter is connected with the air outlet I of the compressor after passing through a regulating valve VG11, a first oil separator, a regulating valve VG12, a first condenser, a first subcooler, a regulating valve VC11, a first calorimeter and a regulating valve VG13 in sequence;
the oil return port of the first oil separator is connected with a first oil return path, the tail end of the first oil return path is connected between the first calorimeter and the regulating valve VG13 of the first refrigerant loop after passing through the regulating valve VG14, the regulating valve VG15, the oil cooler and the regulating valve VG16 in sequence, and a first oil return flowmeter is arranged between the regulating valve VG14 and the regulating valve VG 15;
a second refrigerant circuit: one end of the second condenser is connected with an air inlet II of the compressor after passing through a regulating valve VG21, a second oil separator, a regulating valve VG22, a second condenser, a second subcooler, a regulating valve VC21, a second calorimeter and a regulating valve VG23 in sequence, and a second refrigerant flow meter is arranged between the second subcooler and the second calorimeter;
the oil return port of the second oil separator is connected with a second oil return path, the tail end of the second oil return path is connected between the second calorimeter and the regulating valve VG23 of the second refrigerant loop after passing through the regulating valve VG24, the regulating valve VG25, the oil cooler and the regulating valve VG26 in sequence, and a second oil return flowmeter is arranged between the regulating valve VG24 and the regulating valve VG 25.
The main parameters involved in the performance test of the compressor of the present invention are as follows.
Suction pressure: the air pressure of the air suction port of the compressor;
exhaust pressure: gas pressure at compressor discharge;
valve front pressure: the compressor is at a pressure before the evaporator expansion valve in the refrigeration cycle;
inhalation temperature: the refrigerant temperature of the compressor suction port;
exhaust temperature: a refrigerant temperature at a compressor discharge;
valve pre-temperature: the temperature of the compressor before the evaporator expansion valve in the refrigeration cycle;
refrigerant flow rate: the mass flow rate of the refrigerant flowing in the refrigerant loop;
oil return flow rate: and the oil flow returns to the air suction port of the compressor through an oil return path after the oil separator is processed.
The present invention employs a second refrigerant calorimeter method for compressor performance testing, wherein,
the first condenser and the second condenser respectively control the exhaust pressure of the exhaust port I and the exhaust port II of the double-suction double-row compressor;
the first subcooler and the second subcooler respectively control the valve front temperature before the regulating valve VC11 on the first refrigerant circuit and the valve front temperature before the regulating valve VC21 on the second refrigerant circuit;
the first calorimeter and the second calorimeter respectively control the air suction temperature or enthalpy increasing temperature before the first air suction port and the second air suction port of the double-suction double-row compressor by controlling the respective electric heating quantity;
when a calorimeter method is adopted, the regulating valves VC11 and VC21 respectively control the suction pressure before the first suction port and the second suction port of the double-suction double-row compressor through respective opening degrees;
the regulating valves VG15 and VG25 respectively regulate the oil return flow of the first oil return channel and the second oil return channel through the opening degrees of the regulating valves VG15 and VG 25;
the first refrigerant flow meter and the second refrigerant flow meter respectively test the refrigerant mass flow of the first refrigerant loop and the second refrigerant loop by adopting high-precision mass flow meters;
the first oil separator and the second oil separator separate the refrigerant from the first exhaust port and the second exhaust port of the double-suction double-row compressor from oil, so that the authenticity and the accuracy of the refrigerant mass flow test are ensured;
the first oil return flowmeter and the second oil return flowmeter respectively test the actual oil return quantity of the first air suction port and the second air suction port of the double-suction double-row compressor;
the oil cooler is used for adjusting the oil return temperature of the first oil return path and the second oil return path.
The testing device provided by the invention realizes independent control of various parameters in two refrigerant loops of the double-suction double-row compressor, and the performance of the compressor can be tested by adopting a second refrigerant calorimeter method. In addition, the invention can be matched with a multi-way regulating valve to realize the conversion between the gas ring method test and the calorimeter test so as to realize the unsteady state test of the compressor such as the rapid start-stop state, the sweep frequency state and the like, and the invention is preferably designed as follows:
according to the invention, two ends of a regulating valve VG12 of a first refrigerant loop are connected through a first bypass branch I, the first bypass branch I is provided with a regulating valve VC12, a first bypass branch J is connected between the regulating valve VG12 of the first refrigerant loop and a first condenser, the tail end of the first bypass branch J is connected between a regulating valve VC11 of the first refrigerant loop and a first calorimeter, and a regulating valve VC13 is arranged on the first bypass branch J;
the two ends of the regulating valve VG22 of the second refrigerant loop are connected through a second bypass branch O, the second bypass branch O is provided with a regulating valve VC22, a second bypass branch P is connected between the regulating valve VG22 of the second refrigerant loop and the second condenser, the tail end of the second bypass branch P is connected between the regulating valve VC21 of the second refrigerant loop and the second calorimeter, and the second bypass branch P is provided with a regulating valve VC23.
When calorimeter method is adopted, the regulating valves VC12, VC13, VC22 and VC23 are all closed.
When the gas ring method is adopted, the regulating valves VG12 and VG22 are closed, the opening degree adjustment of the regulating valves VC12 and VC22 is used for respectively controlling the exhaust pressure of the first exhaust port and the second exhaust port of the double-suction double-row compressor, the opening degree adjustment of the regulating valves VC13 and VC23 is used for respectively controlling the suction pressure of the first suction port and the second suction port of the double-suction double-row compressor, and the opening degree adjustment of the regulating valves VC11 and VC21 is used for respectively controlling the suction temperature of the first suction port and the second suction port of the double-suction double-row compressor.
The invention can also be used for the following preferable improved design and performance test of double-suction single-row compressors, single-suction double-row compressors, double-suction single-row compressors and single-suction single-row compressors. The specific scheme is as follows:
the first oil return path is provided with a regulating valve VG17 on a pipeline at the rear end of the regulating valve VG16, the second oil return path is connected with a first middle branch path provided with a regulating valve VG27 between the oil cooler and the regulating valve VG26, and the tail end of the first middle branch path is connected between the regulating valve VG16 and the regulating valve VG17 of the first oil return path.
The second refrigerant loop is provided with a regulating valve V3 between the second subcooler and the second refrigerant flowmeter, a regulating valve V4 is arranged between the second refrigerant flowmeter and the second calorimeter, a second middle branch circuit provided with the regulating valve V1 is connected between the second refrigerant flowmeter and the regulating valve V4, and the tail end of the second middle branch circuit is connected between the first subcooler and the first refrigerant flowmeter of the first refrigerant loop.
In the invention, a third middle branch circuit provided with a regulating valve V2 is connected between the first subcooler and the first refrigerant flowmeter of the first refrigerant loop, and the tail end of the third middle branch circuit is connected between the second subcooler and the second refrigerant flowmeter of the second refrigerant loop.
The first condenser, the first subcooler, the second condenser, the second subcooler and the oil cooler are all connected with a water chilling unit through respective adjustable water circulation pipelines. And controlling circulating water flow which is led into the first condenser, the first subcooler, the second condenser, the second subcooler and the oil cooler through valves with adjustable opening degrees so as to realize adjustment of all parameters.
The invention discloses a device for controlling the temperature of a first refrigerant circuit, which is characterized in that a temperature sensor T11 and a pressure sensor P11 are arranged at a first connection end of the first refrigerant circuit and an exhaust port of a compressor to obtain the exhaust temperature and the exhaust pressure of the first exhaust port, a temperature sensor T12 and a pressure sensor P12 are arranged at a first connection end of the first refrigerant circuit and an air suction port of the compressor to obtain the air suction temperature and the air suction pressure of the air suction port, and a temperature sensor T13 and a pressure sensor P13 are arranged between a first refrigerant flowmeter and a regulating valve VC11 of the first refrigerant circuit to obtain the valve front temperature and the valve front pressure of the first refrigerant circuit;
the second refrigerant circuit is provided with a temperature sensor T21 and a pressure sensor P21 at the second connection end of the air outlet of the compressor to obtain the exhaust temperature and the exhaust pressure of the second air outlet, the second connection end of the second refrigerant circuit and the air suction port of the compressor is provided with a temperature sensor T22 and a pressure sensor P22 to obtain the suction temperature and the suction pressure of the second air suction port, and a temperature sensor T23 and a pressure sensor P23 are arranged between a second refrigerant flowmeter and a regulating valve VC21 of the second refrigerant circuit to obtain the valve front temperature and the valve front pressure of the second refrigerant circuit.
The first refrigerant loop is provided with a temperature sensor T14 and a pressure sensor P14 at the outlet end of the first calorimeter so as to accurately acquire the temperature and the pressure of the outlet of the first calorimeter and accurately calculate the enthalpy change of the inlet end and the outlet end of the first calorimeter;
the second refrigerant loop is provided with a temperature sensor T24 and a pressure sensor P24 at the outlet end of the second calorimeter so as to accurately acquire the temperature and the pressure of the outlet of the second calorimeter and accurately calculate the enthalpy change of the inlet end and the outlet end of the second calorimeter.
The first oil return channel is provided with a temperature sensor T15 between the oil cooler and the regulating valve VG16 so as to acquire the oil return temperature of the first oil return channel;
the second oil return path is provided with a temperature sensor T25 between the oil cooler and the regulator valve VG26 to obtain the oil return temperature of the second oil return path.
The temperature sensor T16 and the pressure sensor P16 are arranged at the rear end of the regulating valve VC13 to obtain the temperature and the pressure of the first bypass branch J, and a basis is provided for regulating the opening of the regulating valve VC13 in a gas ring method;
the second bypass branch P is provided with a temperature sensor T26 and a pressure sensor P26 at the rear end of the regulating valve VC23 so as to acquire the temperature and the pressure of the second bypass branch P, and a basis is provided for regulating the opening of the regulating valve VC23 in the gas ring method.
The invention has the beneficial effects that:
1. according to the testing device, two refrigerant loops are constructed for the double-suction double-row compressor, so that each parameter on the refrigerant loops can be independently controlled, and the performance of the double-suction double-row compressor and the accuracy of endurance test data are ensured.
2. The invention is matched with a multi-path regulating valve to realize the conversion between the gas ring method test and the calorimeter test, and the gas ring method is used for realizing the unsteady state test such as the rapid start-stop state and the sweep frequency state of the compressor.
3. According to the invention, by arranging the plurality of regulating valves, performance tests of the double-suction single-row compressor, the single-suction double-row compressor, the double-suction single-row compressor and the single-suction single-row compressor can be realized, and the universality of the testing device is improved.
Drawings
FIG. 1 is a schematic view of a double suction double row compressor;
FIG. 2 is a schematic diagram of a single suction double row compressor;
FIG. 3 is a schematic illustration of a double suction single row compression face;
FIG. 4 is a general diagram of the working principle of the performance test device of the double suction double row compressor of the present invention;
FIG. 5 is a schematic diagram of a condenser, subcooler of the present invention;
FIG. 6 is a schematic diagram of a chiller of the present invention coupled to the condenser and subcooler of FIG. 5;
FIG. 7 is a schematic diagram of the operation of a double suction double row compressor performance test;
FIG. 8 is a schematic diagram of the operation of a single suction double row compressor performance test;
FIG. 9 is a schematic diagram of the operation of a performance test of a double suction single row compressor;
fig. 10 is a schematic diagram of the operation of a single suction single discharge compressor performance test.
Detailed Description
The following detailed description of the present invention is presented in conjunction with the drawings and examples to enable one of ordinary skill in the art to better understand and practice the present invention.
As shown in fig. 4 to 10, a performance test apparatus for a double suction double row compressor includes:
a first refrigerant circuit: one end of the first refrigerant flow meter is connected with the first air outlet of the compressor, and the other end of the first refrigerant flow meter is connected with the first air inlet of the compressor after passing through the regulating valve VG11, the first oil separator 14, the regulating valve VG12, the first condenser 11, the first subcooler 12, the regulating valve VC11, the first calorimeter 13 and the regulating valve VG13 in sequence, and a first refrigerant flow meter 15 is arranged between the first subcooler 12 and the first calorimeter 13;
the oil return port of the first oil separator 14 is connected with a first oil return path, the tail end of the first oil return path is connected between the first calorimeter 13 and the regulating valve VG13 of the first refrigerant loop after passing through the regulating valve VG14, the regulating valve VG15, the oil cooler 3 and the regulating valve VG16 in sequence, and a first oil return flow meter 16 is arranged between the regulating valve VG14 and the regulating valve VG 15;
a second refrigerant circuit: one end of the second refrigerant flow meter is connected with a second air outlet of the compressor, and the second air outlet of the compressor is connected with the second air inlet of the compressor after passing through a regulating valve VG21, a second oil separator 24, a regulating valve VG22, a second condenser 21, a second subcooler 22, a regulating valve VC21, a second calorimeter 23 and a regulating valve VG23 in sequence, and a second refrigerant flow meter 25 is arranged between the second subcooler 22 and the second calorimeter 23;
the oil return port of the second oil separator 24 is connected with a second oil return path, and the tail end of the second oil return path is connected between a second calorimeter 23 and the regulating valve VG23 of the second refrigerant loop after passing through the regulating valve VG24, the regulating valve VG25, the oil cooler 3 and the regulating valve VG26 in sequence, and a second oil return flow meter 26 is arranged between the regulating valve VG24 and the regulating valve VG 25.
The compressor performance test was performed using a second refrigerant calorimeter method, wherein,
the first condenser 11 and the second condenser 21 respectively control the exhaust pressure of the first exhaust port and the second exhaust port of the double-suction double-row compressor A;
the first subcooler 12 and the second subcooler 22 respectively control the pre-valve temperature before the regulating valve VC11 in the first refrigerant circuit and the pre-valve temperature before the regulating valve VC21 in the second refrigerant circuit;
the first calorimeter 13 and the second calorimeter 23 respectively control the air suction temperature or the enthalpy increasing temperature before the first air suction port and the second air suction port of the double-suction double-row compressor A by controlling the respective electric heating quantity;
when a calorimeter method is adopted, the regulating valves VC11 and VC21 respectively control the suction pressure before the first suction port and the second suction port of the double-suction double-row compressor A through respective opening degrees;
the regulating valves VG15 and VG25 respectively regulate the oil return flow of the first oil return channel and the second oil return channel through the opening degrees of the regulating valves VG15 and VG 25;
the first refrigerant flow meter 15 and the second refrigerant flow meter 25 respectively test the refrigerant mass flow of the first refrigerant loop and the second refrigerant loop by adopting high-precision mass flow meters;
the first oil separator 14 and the second oil separator 24 separate the refrigerant from the first exhaust port and the second exhaust port of the double-suction double-row compressor A from oil, so that the authenticity and the accuracy of the refrigerant mass flow test are ensured;
the first oil return flow meter 16 and the second oil return flow meter 26 respectively test the actual oil return amounts of the first air suction port and the second air suction port of the double-suction double-row compressor A;
the oil cooler 3 is used for adjusting the oil return temperature of the first oil return path and the second oil return path.
The conversion between the gas ring method test and the calorimeter method test can be realized, so that the unsteady state test such as the rapid start-stop state and the sweep frequency state of the compressor can be realized, and the preferred embodiment is as follows:
the two ends of the regulating valve VG12 of the first refrigerant loop are connected through a first bypass branch I, the first bypass branch I is provided with a regulating valve VC12, a first bypass branch J is connected between the regulating valve VG12 of the first refrigerant loop and the first condenser 11, the tail end of the first bypass branch J is connected between the regulating valve VC11 of the first refrigerant loop and the first calorimeter 13, and the first bypass branch J is provided with a regulating valve VC13;
the two ends of the regulating valve VG22 of the second refrigerant loop are connected through a second bypass branch O, the second bypass branch O is provided with a regulating valve VC22, a second bypass branch P is connected between the regulating valve VG22 of the second refrigerant loop and the second condenser, the tail end of the second bypass branch P is connected between the regulating valve VC21 of the second refrigerant loop and the second calorimeter 23, and the second bypass branch P is provided with a regulating valve VC23.
When calorimeter method is adopted, the regulating valves VC12, VC13, VC22 and VC23 are all closed.
When the gas ring method is adopted, the regulating valves VG12 and VG22 are closed, the opening degree adjustment of the regulating valves VC12 and VC22 is used for respectively controlling the exhaust pressure of the first exhaust port and the second exhaust port of the double-suction double-row compressor A, the opening degree adjustment of the regulating valves VC13 and VC23 is used for respectively controlling the suction pressure of the first suction port and the second suction port of the double-suction double-row compressor A, and the opening degree adjustment of the regulating valves VC11 and VC21 is used for respectively controlling the suction temperature of the first suction port and the second suction port of the double-suction double-row compressor A.
The embodiment can be used for performance test of double-suction single-row compressors, single-suction double-row compressors, double-suction single-row compressors and single-suction single-row compressors by following preferred design. The method comprises the following steps:
the first oil return path is provided with a regulating valve VG17 on a pipeline at the rear end of the regulating valve VG16, the second oil return path is connected with a first middle branch path provided with a regulating valve VG27 between the oil cooler 3 and the regulating valve VG26, and the tail end of the first middle branch path is connected between the regulating valve VG16 and the regulating valve VG17 of the first oil return path.
The second refrigerant circuit is provided with a regulating valve V3 between the second subcooler 22 and the second refrigerant flowmeter 25, a regulating valve V4 is provided between the second refrigerant flowmeter 25 and the second calorimeter 23, a second middle branch circuit provided with a regulating valve V1 is connected between the second refrigerant flowmeter and the regulating valve V4, and the tail end of the second middle branch circuit is connected between the first subcooler 12 and the first refrigerant flowmeter 15 of the first refrigerant circuit.
A third middle branch circuit provided with a regulating valve V2 is connected between the first subcooler 12 and the first refrigerant flow meter 15 of the first refrigerant circuit, and the end of the third middle branch circuit is connected between the second subcooler 22 and the second refrigerant flow meter 25 of the second refrigerant circuit.
The first condenser 11, the first subcooler 12, the second condenser 21, the second subcooler 22 and the oil cooler 3 are all connected with the water chiller 5 through respective adjustable water circulation pipelines. The circulating water flow and the water temperature which are led into the first condenser 11, the first subcooler 12, the second condenser 21, the second subcooler 22 and the oil cooler 3 are controlled through valves with adjustable opening degrees, the water flow and the refrigerant or the oil return are subjected to heat exchange through controllable water flow and oil return to realize adjustment of various parameters, particularly, as shown IN fig. 5 and 6, the first condenser 11 is connected with the water chiller 5 through a connector 1OUT and a connector 1IN, the first subcooler 12 is connected with the water chiller 5 through a connector 2OUT and a connector 2IN, the second condenser 21 is connected with the water chiller 5 through a connector 3OUT and a connector 3IN, the connecting pipe is correspondingly provided with a regulating valve WVCTW-D, a regulating valve WVSTW-X and a regulating valve WVSRW-X, and the water temperature controllers HEAC-D, HEAC-X and the water temperature controllers HEAS-X are correspondingly arranged on the connecting pipe respectively, and the water chiller 5 are used for adjusting the water temperature of various circulating pipelines.
A temperature sensor T11 and a pressure sensor P11 are arranged at the first connecting end of the first refrigerant loop and the first exhaust port of the compressor to obtain the first exhaust temperature and the first exhaust pressure, a temperature sensor T12 and a pressure sensor P12 are arranged at the first connecting end of the first refrigerant loop and the first suction port of the compressor to obtain the first suction temperature and the first suction pressure of the suction port, and a temperature sensor T13 and a pressure sensor P13 are arranged between the first refrigerant flowmeter of the first refrigerant loop and the regulating valve VC11 to obtain the first valve front temperature and the first valve front pressure of the first refrigerant loop;
the second refrigerant circuit is provided with a temperature sensor T21 and a pressure sensor P21 at the second connection end of the air outlet of the compressor to obtain the exhaust temperature and the exhaust pressure of the second air outlet, the second connection end of the second refrigerant circuit and the air suction port of the compressor is provided with a temperature sensor T22 and a pressure sensor P22 to obtain the suction temperature and the suction pressure of the second air suction port, and a temperature sensor T23 and a pressure sensor P23 are arranged between a second refrigerant flowmeter and a regulating valve VC21 of the second refrigerant circuit to obtain the valve front temperature and the valve front pressure of the second refrigerant circuit.
The first refrigerant loop is provided with a temperature sensor T14 and a pressure sensor P14 at the outlet end of the first calorimeter 13 so as to accurately acquire the temperature and the pressure of the outlet of the first calorimeter 13 and accurately calculate the enthalpy change of the inlet end and the outlet end of the first calorimeter 13;
the second refrigerant loop is provided with a temperature sensor T24 and a pressure sensor P24 at the outlet end of the second calorimeter 23, so as to accurately obtain the temperature and pressure of the outlet of the second calorimeter 23, and accurately calculate the enthalpy change between the inlet end and the outlet end of the second calorimeter 23.
The first oil return channel is provided with a temperature sensor T15 between the oil cooler 3 and the regulating valve VG16 so as to acquire the oil return temperature of the first oil return channel;
the second oil return path is provided with a temperature sensor T25 between the oil cooler 3 and the regulator valve VG26 to obtain the oil return temperature of the second oil return path.
The temperature sensor T16 and the pressure sensor P16 are arranged at the rear end of the regulating valve VC13 to obtain the temperature and the pressure of the first bypass branch J, and a basis is provided for regulating the opening of the regulating valve VC13 in a gas ring method;
the second bypass branch P is provided with a temperature sensor T26 and a pressure sensor P26 at the rear end of the regulating valve VC23 so as to acquire the temperature and the pressure of the second bypass branch P, and a basis is provided for regulating the opening of the regulating valve VC23 in the gas ring method.
Test example 1: performance and durability testing of double suction double row compressors using a second refrigerant calorimeter method
Referring to fig. 4, the principle of the test device for the double suction double row compressor a is shown in fig. 7 after the regulating valves V1 and V2 are closed, wherein the regulating valves VC12, VC13, VC22, VC23 and VG27 are all closed. A first refrigerant loop and a first oil return path are formed between a first exhaust port and a first air suction port of the double-suction double-row compressor A, and a second refrigerant loop and a second oil return path are formed between a second exhaust port and a second air suction port. The exhaust pressure of the first exhaust port on the first refrigerant loop is controlled by the first condenser 11, the suction pressure of the first suction port is controlled by the opening of the regulating valve VC11, the suction temperature of the first suction port is controlled by the first calorimeter 13, the pre-valve temperature of the regulating valve VC11 is controlled by the first subcooler 12, the oil return temperature of the first oil return path is controlled by the oil cooler 3, and the oil return amount at the first oil return flowmeter 16 is controlled by the opening of the regulating valve VG 15; the exhaust pressure of the second exhaust port on the second refrigerant circuit is controlled by the second condenser 21, the suction pressure of the second suction port is controlled by the opening of the regulating valve VC21, the suction temperature of the second suction port is controlled by the second calorimeter 23, the pre-valve temperature of the regulating valve VC21 is controlled by the second subcooler 22, the oil return temperature of the second oil return circuit is controlled by the oil cooler 3, the oil return amount at the second oil return meter 26 is controlled by the opening of the regulating valve VG25, the refrigerant flow and enthalpy change of the first refrigerant circuit and the second refrigerant circuit are obtained by adopting a second refrigerant calorimeter method under different working conditions through independent control of the parameters, the accurate results of the performances such as the refrigerating capacity, the heating capacity, the power, the volumetric efficiency and the like of the compressor can be obtained, and the double suction double-row compressor A can be tested under the specified conditions by using the testing device, if the compressor noise needs to be tested, and the compressor is placed in the silencing room 4 for testing.
Test example 2: unsteady state working condition test for double-suction double-row compressor by adopting gas ring method
On the basis of test example 1, the regulating valves VG12 and VG22 were closed, the regulating valves VC12, VC13, VC22 and VC23 were opened, and the internal heating of the first calorimeter 13 and the second calorimeter 23 was closed, which is different from test example 1in that at this time, the discharge pressure of the first discharge port on the first refrigerant circuit was controlled by the opening degree of the regulating valve VC12, the suction pressure of the first discharge port was controlled by the opening degree of the regulating valve VC13, the suction temperature of the first discharge port was controlled by the opening degree of the regulating valve VC11, the discharge pressure of the second discharge port on the second refrigerant circuit was controlled by the opening degree of the regulating valve VC22, the suction pressure of the second discharge port was controlled by the opening degree of the regulating valve VC23, and the suction temperature of the second discharge port was controlled by the opening degree of the regulating valve VC 21. The performance test can be carried out on unsteady working conditions such as a quick start-stop working condition, a sweep frequency working condition and the like of the double-suction double-row compressor by adopting a gas ring method.
Test example 3: performance and durability testing of single suction double row compressors using a second refrigerant calorimeter method
Referring to fig. 4, after the adjusting valves V2, VC12, VC13, VC21, VC22, VC23, V4, and VG26 are closed, the test apparatus of the single suction double row compressor B is obtained, as shown in fig. 8, in which the first refrigerant circuit and the first oil return circuit are the same as those of test example 1, the refrigerant at the second exhaust port enters the first oil return circuit through the adjusting valve VG21, the second oil separator 24, the adjusting valve VG22, the second condenser 21, the second subcooler 22, the adjusting valve V3, and the second refrigerant flow meter 25, and then enters the first oil return circuit through the adjusting valve VG24, the second oil return flow meter 26, the adjusting valve VG25, the oil cooler 3, and the adjusting valve 27 of the first intermediate branch, and finally returns to the first suction port through the adjusting valve V1 of the second intermediate branch before reaching the first refrigerant flow meter 15 of the first refrigerant circuit. The adjustment principle of each parameter in the test example 3 is the same as that of the test example 1, and is not repeated here, and the method can be used for testing the performance and durability of the single-suction double-row compressor B.
Test example 4: performance and durability testing of double suction single row compressors using a second refrigerant calorimeter method
Referring to fig. 4, after closing the adjusting valves V1, V3, VG27, VC12, and VC13, a test apparatus for the double suction single discharge compressor C is obtained, as shown in fig. 9, the first oil return path is the same as that of test example 1, except that in test example 1, a third intermediate branch is communicated between the first subcooler 12 and the first refrigerant flow meter 15 of the first refrigerant circuit, and part of the refrigerant from the first exhaust port is returned to the suction port two of the double suction single discharge compressor C through the adjusting valve V2, the second refrigerant flow meter 25, the adjusting valve VC21, the adjusting valve V4, the second calorimeter 23, and the adjusting valve VG23 of the third intermediate branch. The control principle of each parameter is the same as that of test example 1, and the performance and durability of the double suction single row compressor C can be tested.
Test example 5: unsteady state working condition test for double-suction single-row compressor by adopting gas ring method
As shown in fig. 9, on the basis of test example 4, the regulating valve VG12 is closed, the internal heating of the first calorimeter 13 is closed, the regulating valves VC12 and VC13 are opened, the suction pressure of the first suction port is controlled by the opening degree of the regulating valve VC13, the suction temperature of the first suction port is controlled by the regulating valve VC11, the suction pressure of the second suction port is controlled by the opening degree of the regulating valve VC21, the suction temperature of the second suction port is controlled by the second calorimeter 23, and the control principle of the other parameters is the same as that of test example 2, so that the performance test can be performed on the unsteady conditions such as the quick start-stop condition, the sweep frequency condition and the like of the double suction single-row compressor by adopting the gas ring method.
Test example 6: performance and durability testing of single suction single discharge compressors using a second refrigerant calorimeter method
In this test example, the single suction and single discharge compressor D has only one first suction port and one first discharge port. The test device for the single suction single discharge compressor D shown in fig. 10 was obtained by controlling the opening and closing of each control valve, and the control valves VC12 and VC13 were closed, which was different from the test example 1in that only the first refrigerant circuit and the first oil return circuit were formed between the first gas outlet port and the first gas inlet port, and the operation principle was the same as that of the test example 1.
Test example 7: unsteady state working condition test for single-row single-suction compressor by adopting gas ring method
As shown in fig. 10, the control valve VG12 was closed, the control valve VC12 and the control valve VC13 were opened, and only the first refrigerant circuit and the first oil return circuit similar to those in test example 2 were formed, and the operation principle thereof was similar to that in test example 2.
The invention can realize the performance and durability tests of double-suction double-row compressors, single-suction double-row compressors, double-suction single-row compressors and single-suction single-row compressors, and can be converted between a calorimeter method and a gas ring method, thereby realizing the test under the unsteady state working condition of the compressors.
The above embodiments are merely preferred embodiments of the present invention, but they should not be construed as limiting the invention, and any modifications and improvements made on the basis of the inventive concept should fall within the scope of the invention, which is defined by the claims.
Claims (10)
1. A double suction double row compressor performance testing device, comprising:
a first refrigerant circuit: one end of the first refrigerant flow meter is connected with an air outlet I of the compressor, and the other end of the first refrigerant flow meter is connected with the air outlet I of the compressor after passing through a regulating valve VG11, a first oil separator, a regulating valve VG12, a first condenser, a first subcooler, a regulating valve VC11, a first calorimeter and a regulating valve VG13 in sequence;
the oil return port of the first oil separator is connected with a first oil return path, the tail end of the first oil return path is connected between the first calorimeter and the regulating valve VG13 of the first refrigerant loop after passing through the regulating valve VG14, the regulating valve VG15, the oil cooler and the regulating valve VG16 in sequence, and a first oil return flowmeter is arranged between the regulating valve VG14 and the regulating valve VG 15;
a second refrigerant circuit: one end of the second condenser is connected with an air inlet II of the compressor after passing through a regulating valve VG21, a second oil separator, a regulating valve VG22, a second condenser, a second subcooler, a regulating valve VC21, a second calorimeter and a regulating valve VG23 in sequence, and a second refrigerant flow meter is arranged between the second subcooler and the second calorimeter;
the oil return port of the second oil separator is connected with a second oil return path, the tail end of the second oil return path is connected between the second calorimeter and the regulating valve VG23 of the second refrigerant loop after passing through the regulating valve VG24, the regulating valve VG25, the oil cooler and the regulating valve VG26 in sequence, and a second oil return flowmeter is arranged between the regulating valve VG24 and the regulating valve VG 25.
2. The performance testing device of a double suction double row compressor according to claim 1, wherein: the two ends of the regulating valve VG12 of the first refrigerant loop are connected through a first bypass branch I, the first bypass branch I is provided with a regulating valve VC12, a first bypass branch J is connected between the regulating valve VG12 of the first refrigerant loop and a first condenser, the tail end of the first bypass branch J is connected between the regulating valve VC11 of the first refrigerant loop and a first calorimeter, and the first bypass branch J is provided with a regulating valve VC13;
the two ends of the regulating valve VG22 of the second refrigerant loop are connected through a second bypass branch O, the second bypass branch O is provided with a regulating valve VC22, a second bypass branch P is connected between the regulating valve VG22 of the second refrigerant loop and the second condenser, the tail end of the second bypass branch P is connected between the regulating valve VC21 of the second refrigerant loop and the second calorimeter, and the second bypass branch P is provided with a regulating valve VC23.
3. The double suction double row compressor performance testing apparatus according to claim 2, wherein: the first oil return path is provided with a regulating valve VG17 on a pipeline at the rear end of the regulating valve VG16, the second oil return path is connected with a first middle branch path provided with a regulating valve VG27 between the oil cooler and the regulating valve VG26, and the tail end of the first middle branch path is connected between the regulating valve VG16 and the regulating valve VG17 of the first oil return path.
4. The performance test device for double suction double row compressor according to claim 3, wherein: the second refrigerant loop is provided with a regulating valve V3 between the second subcooler and the second refrigerant flowmeter, a regulating valve V4 is arranged between the second refrigerant flowmeter and the second calorimeter, a second middle branch circuit provided with a regulating valve V1 is connected between the second refrigerant flowmeter and the regulating valve V4, and the tail end of the second middle branch circuit is connected between the first subcooler and the first refrigerant flowmeter of the first refrigerant loop.
5. The performance testing device of double suction double row compressor according to claim 4, wherein: a third middle branch circuit provided with a regulating valve V2 is connected between the first subcooler and the first refrigerant flowmeter of the first refrigerant loop, and the tail end of the third middle branch circuit is connected between the second subcooler and the second refrigerant flowmeter of the second refrigerant loop.
6. The performance test device for double suction double row compressor according to any one of claims 1 to 5, wherein: the first condenser, the first subcooler, the second condenser, the second subcooler and the oil cooler are all connected with a water chilling unit through respective adjustable water circulation pipelines.
7. The performance testing device of double suction double row compressor according to claim 6, wherein: a temperature sensor T11 and a pressure sensor P11 are arranged at the first connecting end of the first refrigerant loop and the exhaust port of the compressor, a temperature sensor T12 and a pressure sensor P12 are arranged at the first connecting end of the first refrigerant loop and the air suction port of the compressor, and a temperature sensor T13 and a pressure sensor P13 are arranged between a first refrigerant flowmeter of the first refrigerant loop and the regulating valve VC 11;
the second refrigerant circuit is provided with a temperature sensor T21 and a pressure sensor P21 at the second connection end of the exhaust port of the compressor, the second connection end of the second refrigerant circuit and the air suction port of the compressor is provided with a temperature sensor T22 and a pressure sensor P22, and a temperature sensor T23 and a pressure sensor P23 are arranged between a second refrigerant flowmeter of the second refrigerant circuit and the regulating valve VC 21.
8. The performance testing device of double suction double row compressor according to claim 7, wherein: the first refrigerant loop is provided with a temperature sensor T14 and a pressure sensor P14 at the outlet end of the first calorimeter;
the second refrigerant loop is provided with a temperature sensor T24 and a pressure sensor P24 at the outlet end of the second calorimeter.
9. The performance testing device of double suction double row compressor according to claim 8, wherein: the first oil return path is provided with a temperature sensor T15 between the oil cooler and the regulating valve VG 16;
the second oil return line is provided with a temperature sensor T25 between the oil cooler and the regulator valve VG 26.
10. The double suction double row compressor performance testing apparatus according to claim 2, wherein: the first bypass branch J is provided with a temperature sensor T16 and a pressure sensor P16 at the rear end of the regulating valve VC13;
the second bypass path P is provided with a temperature sensor T26 and a pressure sensor P26 at the rear end of the regulating valve VC23.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311039212.6A CN117249077A (en) | 2023-08-17 | 2023-08-17 | Performance test device for double-suction double-row compressor |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202311039212.6A CN117249077A (en) | 2023-08-17 | 2023-08-17 | Performance test device for double-suction double-row compressor |
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