JB/T 3165-1999 Thermal performance test of centrifugal and axial flow blowers and compressors
Some standard content:
JB/T3165—1999
This standard is a revision of JB3165
6-82 "Thermal Performance Test of Centrifugal and Axial Blowers and Compressors". Compared with JB3165--82, the main technical content of this standard has been changed as follows: Appendix A of the original standard is cancelled, and its content is replaced by the relevant inlet collector part of the flow measurement of the referenced standards GB/T2624-1993 and GB/T1236-1985 respectively; - Appendix B of the original standard is changed to Appendix A of this standard; Appendix C is changed to Appendix B of this standard; - A chapter on reference standards is added.
Appendix A and Appendix B of this standard are both informative appendices. This standard replaces JB3165-82 from the date of implementation. This standard is proposed and managed by the National Technical Committee for Standardization of Fans. The responsible drafting unit of this standard: Shenyang Blower Research Institute. The main drafters of this standard: Wang Changxiang, Kong Fanwen, Guo Qingfu. 75
1 Scope
Machinery Industry Standard of the People's Republic of China
Centrifugal & Axial Blower and Compressor
Thermodynamic Performance Test
Thermodynamic Performance Test for Centrifugal & Axial Blower and Compressor
1.1 This standard specifies the test method for the thermal performance test of centrifugal & axial blower and compressor. JB/T 3165
5—1999
Replaces JB3165-82
1.2 This standard is applicable to the thermal performance test of centrifugal & axial blower, compressor and exhauster (hereinafter referred to as compressor) with a pressure ratio greater than 1.15 and known gas physical parameters by the manufacturer. 1.3 Determine the thermodynamic performance parameters of the compressor under design conditions through tests and calculations: a) compressor inlet volume flow;
b) compressor boost or pressure ratio;
c) compressor shaft power;
d) compressor efficiency;
e) compressor surge limit.
Draw the relationship curve between the compressor flow and boost (or pressure ratio), shaft power and efficiency at the design speed from the above performance parameters: If the compressor is tested in sections (cylinders), its performance can be expressed by the performance curve of each section (cylinder), or by the performance curve of the whole machine obtained by superimposing the performance curves of each section (cylinder). 1.4 The measuring instruments and measuring methods recommended in this standard are the minimum requirements and do not restrict the use of other measuring instruments and measuring methods with equal or higher accuracy.
2 Referenced standards
The provisions contained in the following standards constitute the provisions of this standard through reference in this standard. When this standard is published, the versions shown are valid. All standards are subject to revision. Parties using this standard should explore the possibility of using the latest version of the following standards. GB/T1236-1985 Test method for aerodynamic performance of ventilators GB/T 2624--1993
Flow measurement Throttling device Measuring the flow of fluids filling a circular tube with orifice plates, nozzles and venturi tubes 3 Symbols and instructions
The symbols used in this standard are listed in Table 1 and the footnotes to the symbols are listed in Table 2. Approved by the State Machinery Industry Bureau on July 12, 1999
Implemented on January 1, 2000
Impeller outlet width
Air flow velocity
Specific heat of cooling water
Isobaric specific heat
Isochoric specific heat
Isobaric molar specific heat
Isochoric molar specific heat
Throttle hole diameter
Pipeline diameter
Impeller outer diameter
Variable energy head correction
Gravity acceleration
Cooling water volume
Mass flow rate
Leakage mass flow rate
Total gas
Gas static gas
Adiabatic index
Isobaric exponent
Variable temperature index in the figure
JB/T 3165—1999
Cross-sectional area of flow passage
refers to the width of the first-stage centrifugal impeller outlet; the chord length of the top of the first-stage axial flow blade (the characteristic length for calculating the Reynolds number of the compressor) m/s
J/(kg·K)
J/(kmol·K)
kg/min
Air velocity on the cross-sectional area of flow
Cp=Mcp
Throttling element: orifice plate, venturi tube or nozzle reduction diameter refers to the inner diameter of the pipe
h'a-hi
R(Z,T2-Z,T1)
etc. The effective value of the process outlet.
Usually, when bar≤4, it is taken at ~1.0
Torque measuring instrument measurement value
g = 9. 806 65 m/s2
usually refers to the mass flow rate discharged by the compressor. If there is leakage (may leak from the shaft end seal or leak or condensate), the mass flow rate at the inlet and outlet flanges of the compressor will be different. Attention should be paid when converting the inlet and outlet flow rates. When the leakage is less than 1.0%, it can be ignored.
qm=qm2+ZAgm,L+ZAgm.d
refers to the measured mass flow rate of the shaft end seal or condensate. If the actual measurement is difficult, it can also be obtained by calculation.
For ideal gas,, = two
forbidden constant
8314.4Zm/
molecular weight
compressor Mach number
gas component mass percentage
variable||tt in the pV diagram t||Volume index
Throttling differential pressure
Absolute pressure
Atmospheric pressure
Critical pressure
Upstream pressure
Comparative pressure
Gas power
Heat loss power
Leakage loss power
Internal power
JB/T3165-1999
Table 1 (continued)
kg/kmo!
The mass of a molecule of a substance is expressed in units of the atomic weight of carbon-12, 12.000
VkuRZT
pV\=constant
Ym-m(1+XM)
For ideal gas:
Ig/ pa
(-k(l -~ npot)
The difference in static pressure at the upstream and downstream pressure tappings of the orifice plate, nozzle or venturi tube. This standard refers to the absolute total pressure: b=plp.tpaSee 5.5.2
Measured value of static pressure on the pipeline wall
Absolute static pressure measured at the upstream pressure tapping of the throttling element: pup=p.+pc.apPr = pa/pe(psn
Absolute static pressure）
P=qvipiWm/(6×10*)
The gas power of different compression processes is indicated by footnotes: PPal =
qvip.Wm.Pal
6×104
gvip.w..i
6×104
The sum of the outer surface area of the casing and the outer surface area of a section of the pipeline from the outlet temperature measuring point to the casing outlet flange. The heat loss power transmitted to the surrounding atmosphere: P.=aS.(tma-- t.)/1000
tMe—-The average temperature on the outer surface of the casing is usually P0.02P. When.α value: α=14W/(m2, K)The power loss caused by the leakage of the shaft end labyrinth seal; P1.=-EAqm.1AhL/(6X 104)
hl.—The difference between the compressor outlet melt hz and the gas leaking into the shaft end seal
Pu-P+P.-PL-r
Mechanical loss power
Shaft power
Volumetric flow
Gas constant
Compressor Reynolds number
Heat dissipation area
Thermometer temperature
Absolute temperature
Critical temperature
Comparative temperature
Leaf Wheel outer peripheral speed
Specific compression work
Isobaric deviation coefficient
Isothermal deviation coefficient
Compressibility coefficient
JB/T3165—1999
Table 1 (continued)
Power loss caused by friction of bearings, seals (or transmission gears): kw
m°/min
J/(kg·K)
P,=EqmoiCpmiAtail/(6× 10)
Power input at the compressor coupling or transmission gear coupling: P.-Pin+Pr
This standard usually refers to the volume flow rate Rm 8 314 at the compressor inlet stagnant state.4
The sum of the outer surface area of the casing and the outer surface area of the section of the pipeline from the outlet temperature measuring point to the casing outlet flange
T=273.16+t
The specific compression work of different compression processes is shown in the footnotes Wm,rol =
VlaTlp
See Figure A6. For ideal gas, X=0
Z(ap)
See Figure A5. For ideal gas, Y=1
See Figures A1 to A4. For ideal gas, Z=179
Gas efficiency
Internal efficiency
Mechanical efficiency
Effective efficiency
Gas mass density
Dynamic viscosity
Kinematic viscosity
Flow coefficient
Relative humidity
Expansion coefficient
Narrowing diameter ratio
Loss coefficient
JB/T3165—1999
Table 1 (end)
Uncooled compressor:
h --hi
When the compressor is equipped with an exhaust cooler at the outlet of the whole unit or a stage (cylinder): m
7= h,=h,+Q1-2
Heat cooled by the cooler (excluding heat dissipation of the casing) Q1-2 --
The gas efficiency of different compression processes is indicated by footnotes: Pal
hz - hr+Q1-2
h,—h+Q1-2
The internal efficiency of different compression processes is indicated by footnotes: Ppal
nin,Pol =
The ratio of internal power to the effective power at the compressor coupling (or transmission gear coupling):
The ratio of gas power to the effective power at the compressor coupling (or transmission gear coupling):
The effective efficiency of different compression processes is indicated by footnotes: Me.Pol
For ideal gas, Z=1.0
Flow coefficient of throttling element orifice, Venturi tube or nozzle (see GB/T2624)
Expansion coefficient of throttling element orifice, Venturi tube or nozzle (see GB/T2624)
Narrowing diameter ratio of orifice, Venturi tube or nozzle β=d/DTest pipeline or rectifier loss coefficient
Footnote symbol
Footnote meaning
Inlet
Outlet
"Section, 1 Section, Section
Atmospheric state or static
Powerful
Effective
Dry gas
Arithmetic mean
Casing surface
JB/T3165-1999
Usually refers to the compressor inlet flange.
If a suction throttling device belonging to the compressor is directly installed in front of the intake flange, the section in front of the throttling device is the intake port.
For a multi-stage (cylinder) intermediate cooling compressor, when the segment (cylinder) non-cooling test is carried out, the cross section at the intake flange of each segment (cylinder) is the intake port.
For an intermediate gas-filling compressor, the cross section after the main airflow (segment outlet airflow before the gas-filling segment) and the gas-filling are mixed is the gas-filling segment intake port
Usually refers to the compressor outlet flange.
If a cooler belonging to the compressor is installed at the compressor outlet, the cooler outlet cross section is the compressor outlet.
When a multi-stage (cylinder) intermediate cooling compressor is carried out in the segment (cylinder) non-cooling test, the cross section at the outlet flange of each segment (cylinder) is the outlet.
Intermediate air extraction compressor uses the cross section of the outlet of the extraction section as the outlet. Compressor segment number
4 Test equipment and instruments
JB/T3165--- 1999
According to the different test systems (called test benches) connected to the compressor, it can be divided into two types of test benches: open and closed. 4.1 Open test bench
The open test bench uses air as the test gas, and is composed of a test pipeline, a flow measurement pipeline, and a throttle valve. According to the different connection methods between the test pipeline and the compressor inlet and outlet, it can be divided into three types of test devices: intake, outlet, and intake and outlet. 4.1.1 Intake test device (suitable for exhaust compressors): The test pipeline is connected to the compressor inlet end face, and the outlet end is open to the atmosphere (see Figure 1 and Figure 2).
If the air inlet of the compressor intake chamber shown in Figure 2 is horizontal, the test device should be arranged as shown in Figure 1. 4.1.2 Gas outlet test device (applicable to compressors supplying compressed gas): the inlet end face is open to the atmosphere, and the outlet end face is connected to the test pipeline (see Figures 3 and 4).
4.1.3 Gas inlet and outlet test device (applicable to single-stage or multi-stage compressors and intercooled compressor segmented test): the compressor inlet and outlet are connected to the test pipeline (see Figures 5 and 6). 4.2 Closed test bench
The closed test uses gases other than air as test gas, and consists of a test pipeline, a flow measurement pipeline, a connecting pipe, a throttle valve, a cooler and a gas supply device. It is divided into two types of test devices: single-channel and multi-channel closed. 4.2.1 Single-channel closed test device (see Figure 7): Applicable to single-stage or multi-stage uncooled compressor tests from single inlet to single outlet, and segmented tests of compressors with external intercooling. The device in Figure 7 can also be used when the compressor with an external intercooler is tested as a whole machine. If the performance parameters of the middle section need to be measured, the position of the measuring point shall be arranged according to the actual situation of the pipelines before and after the intercooler. 4.2.2 Multi-channel closed test device (see Figure 8 and Figure 9). 4.3 Test pipeline
The test pipeline shall adopt round tubes, and its size, shape and surface requirements shall comply with the following provisions. 4.3.1 The cross-sectional area of the inlet and outlet test pipelines shall be as close as possible to the area of the compressor inlet and outlet flange end faces. If they are different, a conical joint shall be used for connection.
4.3.1.1 The inlet test pipeline uses a convergent conical joint, and the ratio of the two cross-sectional areas shall not exceed 1.0~~1.3. 4.3.1.2 The outlet test pipeline uses a convergent or divergent joint, and the ratio of the two cross-sectional areas shall not exceed 0.7~1.3. 4.3.1.3 The external dimensions of the conical joint refer to the provisions in GB/T1236. 4.3.2 The inner wall of the inlet and outlet test pipelines shall be smooth and free of dust and peeling, and the length of the pipeline shall comply with the provisions of Figures 1 to 9 respectively.
4.3.3 The inlet and outlet test pipelines shall be provided with measuring holes for measuring static pressure and temperature respectively. 4.3.3.1 Holes for measuring static pressure: Drill 4 holes evenly distributed along the circumference on the same cross-section wall of the pipeline. The hole shall be perpendicular to the pipe wall, and the inner wall surface around the junction of the pipe and the hole shall be smooth and free of burrs to avoid blockage. According to the specific conditions of the gas, the diameter of the hole shall be as small as possible, and the maximum shall not exceed 3mm.
4.3.3.2 Holes for measuring temperature: Drill 4 holes evenly distributed along the circumferential direction on the same designated cross-section wall of the pipeline, and each hole is equidistant and staggered 45° from the hole for measuring static pressure.
4.3.4 When the dynamic pressure at the static pressure measurement point is greater than the pressure rise by 5%, 2 holes should be drilled at 90° intervals along the circumferential direction on the cross-section downstream of the static pressure hole for the installation of the dynamic pressure pipe.
4.4 Rectifier and porous plate
4.4.1 Rectifiers for regulating the air flow in pipelines are divided into two types: well-shaped and porous. The dimensions are specified in GB/T1236. 4.4.2 Perforated plate
The number of holes on a perforated plate shall not be less than 500/m, and the number of holes on the entire plate shall not be less than 50. The ratio of the total area of the holes to the cross-sectional area of the pipeline is determined by the following formula:
In the formula: An--total area of the openings of the perforated plate, m; Ap--twice the dynamic pressure of the pipeline.
JB/T3165-—1999
51DppAp
≥10D
JB/T 3165—1999
When measuring without a dynamic pressure tube, it is 10 Dz
JB/T 3165 -- 1999
≥12D2
JB/T 3165--1999rol =
VlaTlp
See Figure A6. For ideal gas, X=0
Z(ap)
See Figure A5. For ideal gas, Y=1
See Figures A1 to A4. For ideal gas, Z=179
Gas efficiency
Internal efficiency
Mechanical efficiency
Effective efficiency
Gas mass density
Dynamic viscosity
Kinematic viscosity
Flow coefficient
Relative humidity
Expansion coefficient
Narrowing diameter ratio
Loss coefficient
JB/T3165—1999
Table 1 (end)
Uncooled compressor:
h --hi
When the compressor is equipped with an exhaust cooler at the outlet of the whole unit or a stage (cylinder): m
7= h,=h,+Q1-2
Heat cooled by the cooler (excluding heat dissipation of the casing) Q1-2 --
The gas efficiency of different compression processes is indicated by footnotes: Pal
hz - hr+Q1-2
h,—h+Q1-2
The internal efficiency of different compression processes is indicated by footnotes: Ppal
nin,Pol =
The ratio of internal power to the effective power at the compressor coupling (or transmission gear coupling):
The ratio of gas power to the effective power at the compressor coupling (or transmission gear coupling):
The effective efficiency of different compression processes is indicated by footnotes: Me.Pol
For ideal gas, Z=1.0
Flow coefficient of throttling element orifice, Venturi tube or nozzle (see GB/T2624)
Expansion coefficient of throttling element orifice, Venturi tube or nozzle (see GB/T2624)
Narrowing diameter ratio of orifice, Venturi tube or nozzle β=d/DTest pipeline or rectifier loss coefficient
Footnote symbol
Footnote meaning
Inlet
Outlet
"Section, 1 Section, Section
Atmospheric state or static
Powerful
Effective
Dry gas
Arithmetic mean
Casing surface
JB/T3165-1999
Usually refers to the compressor inlet flange.
If a suction throttling device belonging to the compressor is directly installed in front of the intake flange, the section in front of the throttling device is the intake port.
For a multi-stage (cylinder) intermediate cooling compressor, when the segment (cylinder) non-cooling test is carried out, the cross section at the intake flange of each segment (cylinder) is the intake port.
For an intermediate gas-filling compressor, the cross section after the main airflow (segment outlet airflow before the gas-filling segment) and the gas-filling are mixed is the gas-filling segment intake port
Usually refers to the compressor outlet flange.
If a cooler belonging to the compressor is installed at the compressor outlet, the cooler outlet cross section is the compressor outlet.
When a multi-stage (cylinder) intermediate cooling compressor is carried out in the segment (cylinder) non-cooling test, the cross section at the outlet flange of each segment (cylinder) is the outlet.
Intermediate air extraction compressor uses the cross section of the outlet of the extraction section as the outlet. Compressor segment number
4 Test equipment and instruments
JB/T3165--- 1999
According to the different test systems (called test benches) connected to the compressor, it can be divided into two types of test benches: open and closed. 4.1 Open test bench
The open test bench uses air as the test gas, and is composed of a test pipeline, a flow measurement pipeline, and a throttle valve. According to the different connection methods between the test pipeline and the compressor inlet and outlet, it can be divided into three types of test devices: intake, outlet, and intake and outlet. 4.1.1 Intake test device (suitable for exhaust compressors): The test pipeline is connected to the compressor inlet end face, and the outlet end is open to the atmosphere (see Figure 1 and Figure 2).
If the air inlet of the compressor intake chamber shown in Figure 2 is horizontal, the test device should be arranged as shown in Figure 1. 4.1.2 Gas outlet test device (applicable to compressors supplying compressed gas): the inlet end face is open to the atmosphere, and the outlet end face is connected to the test pipeline (see Figures 3 and 4).
4.1.3 Gas inlet and outlet test device (applicable to single-stage or multi-stage compressors and intercooled compressor segmented test): the compressor inlet and outlet are connected to the test pipeline (see Figures 5 and 6). 4.2 Closed test bench
The closed test uses gases other than air as test gas, and consists of a test pipeline, a flow measurement pipeline, a connecting pipe, a throttle valve, a cooler and a gas supply device. It is divided into two types of test devices: single-channel and multi-channel closed. 4.2.1 Single-channel closed test device (see Figure 7): Applicable to single-stage or multi-stage uncooled compressor tests from single inlet to single outlet, and segmented tests of compressors with external intercooling. The device in Figure 7 can also be used when the compressor with an external intercooler is tested as a whole machine. If the performance parameters of the middle section need to be measured, the position of the measuring point shall be arranged according to the actual situation of the pipelines before and after the intercooler. 4.2.2 Multi-channel closed test device (see Figure 8 and Figure 9). 4.3 Test pipeline
The test pipeline shall adopt round tubes, and its size, shape and surface requirements shall comply with the following provisions. 4.3.1 The cross-sectional area of the inlet and outlet test pipelines shall be as close as possible to the area of the compressor inlet and outlet flange end faces. If they are different, a conical joint shall be used for connection.
4.3.1.1 The inlet test pipeline uses a convergent conical joint, and the ratio of the two cross-sectional areas shall not exceed 1.0~~1.3. 4.3.1.2 The outlet test pipeline uses a convergent or divergent joint, and the ratio of the two cross-sectional areas shall not exceed 0.7~1.3. 4.3.1.3 The external dimensions of the conical joint refer to the provisions in GB/T1236. 4.3.2 The inner wall of the inlet and outlet test pipelines shall be smooth and free of dust and peeling, and the length of the pipeline shall comply with the provisions of Figures 1 to 9 respectively.
4.3.3 The inlet and outlet test pipelines shall be provided with measuring holes for measuring static pressure and temperature respectively. 4.3.3.1 Holes for measuring static pressure: Drill 4 holes evenly distributed along the circumference on the same cross-section wall of the pipeline. The hole shall be perpendicular to the pipe wall, and the inner wall surface around the junction of the pipe and the hole shall be smooth and free of burrs to avoid blockage. According to the specific conditions of the gas, the diameter of the hole shall be as small as possible, and the maximum shall not exceed 3mm.
4.3.3.2 Holes for measuring temperature: Drill 4 holes evenly distributed along the circumferential direction on the same designated cross-section wall of the pipeline, and each hole is equidistant and staggered 45° from the hole for measuring static pressure.
4.3.4 When the dynamic pressure at the static pressure measurement point is greater than the pressure rise by 5%, 2 holes should be drilled at 90° intervals along the circumferential direction on the cross-section downstream of the static pressure hole for the installation of the dynamic pressure pipe.
4.4 Rectifier and porous plate
4.4.1 Rectifiers for regulating the air flow in pipelines are divided into two types: well-shaped and porous. The dimensions are specified in GB/T1236. 4.4.2 Perforated plate
The number of holes on a perforated plate shall not be less than 500/m, and the number of holes on the entire plate shall not be less than 50. The ratio of the total area of the holes to the cross-sectional area of the pipeline is determined by the following formula:
In the formula: An--total area of the openings of the perforated plate, m; Ap--twice the dynamic pressure of the pipeline.
JB/T3165-—1999
51DppAp
≥10D
JB/T 3165—1999
When measuring without a dynamic pressure tube, it is 10 Dz
JB/T 3165 -- 1999
≥12D2
JB/T 3165--1999rol =
VlaTlp
See Figure A6. For ideal gas, X=0
Z(ap)
See Figure A5. For ideal gas, Y=1
See Figures A1 to A4. For ideal gas, Z=179
Gas efficiency
Internal efficiency
Mechanical efficiency
Effective efficiency
Gas mass density
Dynamic viscosity
Kinematic viscosity
Flow coefficient
Relative humidity
Expansion coefficient
Narrowing diameter ratio
Loss coefficient
JB/T3165—1999
Table 1 (end)
Uncooled compressor:
h --hi
When the compressor is equipped with an exhaust cooler at the outlet of the whole unit or a stage (cylinder): m
7= h,=h,+Q1-2
Heat cooled by the cooler (excluding heat dissipation of the casing) Q1-2 --
The gas efficiency of different compression processes is indicated by footnotes: Pal
hz - hr+Q1-2
h,—h+Q1-2
The internal efficiency of different compression processes is indicated by footnotes: Ppal
nin,Pol =
The ratio of internal power to the effective power at the compressor coupling (or transmission gear coupling):
The ratio of gas power to the effective power at the compressor coupling (or transmission gear coupling):
The effective efficiency of different compression processes is indicated by footnotes: Me.Pol
For ideal gas, Z=1.0
Flow coefficient of throttling element orifice, Venturi tube or nozzle (see GB/T2624)
Expansion coefficient of throttling element orifice, Venturi tube or nozzle (see GB/T2624)
Narrowing diameter ratio of orifice, Venturi tube or nozzle β=d/DTest pipeline or rectifier loss coefficient
Footnote symbol
Footnote meaning
Inlet
Outlet
"Section, 1 Section, Section
Atmospheric state or static
Powerful
Effective
Dry gas
Arithmetic mean
Casing surface
JB/T3165-1999
Usually refers to the compressor inlet flange.
If a suction throttling device belonging to the compressor is directly installed in front of the intake flange, the section in front of the throttling device is the intake port.
For a multi-stage (cylinder) intermediate cooling compressor, when the segment (cylinder) non-cooling test is carried out, the cross section at the intake flange of each segment (cylinder) is the intake port.
For an intermediate gas-filling compressor, the cross section after the main airflow (segment outlet airflow before the gas-filling segment) and the gas-filling are mixed is the gas-filling segment intake port
Usually refers to the compressor outlet flange.
If a cooler belonging to the compressor is installed at the compressor outlet, the cooler outlet cross section is the compressor outlet.
When a multi-stage (cylinder) intermediate cooling compressor is carried out in the segment (cylinder) non-cooling test, the cross section at the outlet flange of each segment (cylinder) is the outlet.
Intermediate air extraction compressor uses the cross section of the outlet of the extraction section as the outlet. Compressor segment number
4 Test equipment and instruments
JB/T3165--- 1999
According to the different test systems (called test benches) connected to the compressor, it can be divided into two types of test benches: open and closed. 4.1 Open test bench
The open test bench uses air as the test gas, and is composed of a test pipeline, a flow measurement pipeline, and a throttle valve. According to the different connection methods between the test pipeline and the compressor inlet and outlet, it can be divided into three types of test devices: intake, outlet, and intake and outlet. 4.1.1 Intake test device (suitable for exhaust compressors): The test pipeline is connected to the compressor inlet end face, and the outlet end is open to the atmosphere (see Figure 1 and Figure 2).
If the air inlet of the compressor intake chamber shown in Figure 2 is horizontal, the test device should be arranged as shown in Figure 1. 4.1.2 Gas outlet test device (applicable to compressors supplying compressed gas): the inlet end face is open to the atmosphere, and the outlet end face is connected to the test pipeline (see Figures 3 and 4).
4.1.3 Gas inlet and outlet test device (applicable to single-stage or multi-stage compressors and intercooled compressor segmented test): the compressor inlet and outlet are connected to the test pipeline (see Figures 5 and 6). 4.2 Closed test bench
The closed test uses gases other than air as test gas, and consists of a test pipeline, a flow measurement pipeline, a connecting pipe, a throttle valve, a cooler and a gas supply device. It is divided into two types of test devices: single-channel and multi-channel closed. 4.2.1 Single-channel closed test device (see Figure 7): Applicable to single-stage or multi-stage uncooled compressor tests from single inlet to single outlet, and segmented tests of compressors with external intercooling. The device in Figure 7 can also be used when the compressor with an external intercooler is tested as a whole machine. If the performance parameters of the middle section need to be measured, the position of the measuring point shall be arranged according to the actual situation of the pipelines before and after the intercooler. 4.2.2 Multi-channel closed test device (see Figure 8 and Figure 9). 4.3 Test pipeline
The test pipeline shall adopt round tubes, and its size, shape and surface requirements shall comply with the following provisions. 4.3.1 The cross-sectional area of the inlet and outlet test pipelines shall be as close as possible to the area of the compressor inlet and outlet flange end faces. If they are different, a conical joint shall be used for connection.
4.3.1.1 The inlet test pipeline uses a convergent conical joint, and the ratio of the two cross-sectional areas shall not exceed 1.0~~1.3. 4.3.1.2 The outlet test pipeline uses a convergent or divergent joint, and the ratio of the two cross-sectional areas shall not exceed 0.7~1.3. 4.3.1.3 The external dimensions of the conical joint refer to the provisions in GB/T1236. 4.3.2 The inner wall of the inlet and outlet test pipelines shall be smooth and free of dust and peeling, and the length of the pipeline shall comply with the provisions of Figures 1 to 9 respectively.
4.3.3 The inlet and outlet test pipelines shall be provided with measuring holes for measuring static pressure and temperature respectively. 4.3.3.1 Holes for measuring static pressure: Drill 4 holes evenly distributed along the circumference on the same cross-section wall of the pipeline. The hole shall be perpendicular to the pipe wall, and the inner wall surface around the junction of the pipe and the hole shall be smooth and free of burrs to avoid blockage. According to the specific conditions of the gas, the diameter of the hole shall be as small as possible, and the maximum shall not exceed 3mm.
4.3.3.2 Holes for measuring temperature: Drill 4 holes evenly distributed along the circumferential direction on the same designated cross-section wall of the pipeline, and each hole is equidistant and staggered 45° from the hole for measuring static pressure.
4.3.4 When the dynamic pressure at the static pressure measurement point is greater than the pressure rise by 5%, 2 holes should be drilled at 90° intervals along the circumferential direction on the cross-section downstream of the static pressure hole for the installation of the dynamic pressure pipe.
4.4 Rectifier and porous plate
4.4.1 Rectifiers for regulating the air flow in pipelines are divided into two types: well-shaped and porous. The dimensions are specified in GB/T1236. 4.4.2 Perforated plate
The number of holes on a perforated plate shall not be less than 500/m, and the number of holes on the entire plate shall not be less than 50. The ratio of the total area of the holes to the cross-sectional area of the pipeline is determined by the following formula:
In the formula: An--total area of the openings of the perforated plate, m; Ap--twice the dynamic pressure of the pipeline.
JB/T3165-—1999
51DppAp
≥10D
JB/T 3165—1999
When measuring without a dynamic pressure tube, it is 10 Dz
JB/T 3165 -- 1999
≥12D2
JB/T 3165--19990
Flow coefficient of throttling element orifice, Venturi tube or nozzle (see GB/T2624)
Expansion coefficient of throttling element orifice, Venturi tube or nozzle (see GB/T2624)
Narrowing diameter ratio of orifice, Venturi tube or nozzle β=d/DTest pipeline or rectifier loss coefficient
Footnote symbol
Footnote meaning
Inlet
Outlet
" Section, 1 Section, Section
Atmospheric state or static
Powerful
Effective
Dry gas
Arithmetic mean
Casing surface
JB/T3165-1999
Usually refers to the compressor inlet flange.
If a suction throttling device belonging to the compressor is directly installed in front of the intake flange, the section in front of the throttling device is the intake port.
For a multi-stage (cylinder) intermediate cooling compressor, when the segment (cylinder) non-cooling test is carried out, the cross section at the intake flange of each segment (cylinder) is the intake port.
For an intermediate gas-filling compressor, the cross section after the main airflow (segment outlet airflow before the gas-filling segment) and the gas-filling are mixed is the gas-filling segment intake port
Usually refers to the compressor outlet flange.
If a cooler belonging to the compressor is installed at the compressor outlet, the cooler outlet cross section is the compressor outlet.
When a multi-stage (cylinder) intermediate cooling compressor is carried out in the segment (cylinder) non-cooling test, the cross section at the outlet flange of each segment (cylinder) is the outlet.
Intermediate air extraction compressor uses the cross section of the outlet of the extraction section as the outlet. Compressor segment number
4 Test equipment and instruments
JB/T3165--- 1999
According to the different test systems (called test benches) connected to the compressor, it can be divided into two types of test benches: open and closed. 4.1 Open test bench
The open test bench uses air as the test gas, and is composed of a test pipeline, a flow measurement pipeline, and a throttle valve. According to the different connection methods between the test pipeline and the compressor inlet and outlet, it can be divided into three types of test devices: intake, outlet, and intake and outlet. 4.1.1 Intake test device (suitable for exhaust compressors): The test pipeline is connected to the compressor inlet end face, and the outlet end is open to the atmosphere (see Figure 1 and Figure 2).
If the air inlet of the compressor intake chamber shown in Figure 2 is horizontal, the test device should be arranged as shown in Figure 1. 4.1.2 Gas outlet test device (applicable to compressors supplying compressed gas): the inlet end face is open to the atmosphere, and the outlet end face is connected to the test pipeline (see Figures 3 and 4).
4.1.3 Gas inlet and outlet test device (applicable to single-stage or multi-stage compressors and intercooled compressor segmented test): the compressor inlet and outlet are connected to the test pipeline (see Figures 5 and 6). 4.2 Closed test bench
The closed test uses gases other than air as test gas, and consists of a test pipeline, a flow measurement pipeline, a connecting pipe, a throttle valve, a cooler and a gas supply device. It is divided into two types of test devices: single-channel and multi-channel closed. 4.2.1 Single-channel closed test device (see Figure 7): Applicable to single-stage or multi-stage uncooled compressor tests from single inlet to single outlet, and segmented tests of compressors with external intercooling. The device in Figure 7 can also be used when the compressor with an external intercooler is tested as a whole machine. If the performance parameters of the middle section need to be measured, the position of the measuring point shall be arranged according to the actual situation of the pipelines before and after the intercooler. 4.2.2 Multi-channel closed test device (see Figure 8 and Figure 9). 4.3 Test pipeline
The test pipeline shall adopt round tubes, and its size, shape and surface requirements shall comply with the following provisions. 4.3.1 The cross-sectional area of the inlet and outlet test pipelines shall be as close as possible to the area of the compressor inlet and outlet flange end faces. If they are different, a conical joint shall be used for connection.
4.3.1.1 The inlet test pipeline uses a convergent conical joint, and the ratio of the two cross-sectional areas shall not exceed 1.0~~1.3. 4.3.1.2 The outlet test pipeline uses a convergent or divergent joint, and the ratio of the two cross-sectional areas shall not exceed 0.7~1.3. 4.3.1.3 The external dimensions of the conical joint refer to the provisions in GB/T1236. 4.3.2 The inner wall of the inlet and outlet test pipelines shall be smooth and free of dust and peeling, and the length of the pipeline shall comply with the provisions of Figures 1 to 9 respectively.
4.3.3 The inlet and outlet test pipelines shall be provided with measuring holes for measuring static pressure and temperature respectively. 4.3.3.1 Holes for measuring static pressure: Drill 4 holes evenly distributed along the circumference on the same cross-section wall of the pipeline. The hole shall be perpendicular to the pipe wall, and the inner wall surface around the junction of the pipe and the hole shall be smooth and free of burrs to avoid blockage. According to the specific conditions of the gas, the diameter of the hole shall be as small as possible, and the maximum shall not exceed 3mm.
4.3.3.2 Holes for measuring temperature: Drill 4 holes evenly distributed along the circumferential direction on the same designated cross-section wall of the pipeline, and each hole is equidistant and staggered 45° from the hole for measuring static pressure.
4.3.4 When the dynamic pressure at the static pressure measurement point is greater than the pressure rise by 5%, 2 holes should be drilled at 90° intervals along the circumferential direction on the cross-section downstream of the static pressure hole for the installation of the dynamic pressure pipe.
4.4 Rectifier and porous plate
4.4.1 Rectifiers for regulating the air flow in pipelines are divided into two types: well-shaped and porous. The dimensions are specified in GB/T1236. 4.4.2 Perforated plate
The number of holes on a perforated plate shall not be less than 500/m, and the number of holes on the entire plate shall not be less than 50. The ratio of the total area of the holes to the cross-sectional area of the pipeline is determined by the following formula:
In the formula: An--total area of the openings of the perforated plate, m; Ap--twice the dynamic pressure of the pipeline.
JB/T3165-—1999
51DppAp
≥10D
JB/T 3165—1999
When measuring without a dynamic pressure tube, it is 10 Dz
JB/T 3165 -- 1999
≥12D2
JB/T 3165--19990
Flow coefficient of throttling element orifice, Venturi tube or nozzle (see GB/T2624)
Expansion coefficient of throttling element orifice, Venturi tube or nozzle (see GB/T2624)
Narrowing diameter ratio of orifice, Venturi tube or nozzle β=d/DTest pipeline or rectifier loss coefficient
Footnote symbol
Footnote meaning
Inlet
Outlet
" Section, 1 Section, Section
Atmospheric state or static
Powerful
Effective
Dry gas
Arithmetic mean
Casing surface
JB/T3165-1999Www.bzxZ.net
Usually refers to the compressor inlet flange.
If a suction throttling device belonging to the compressor is directly installed in front of the intake flange, the section in front of the throttling device is the intake port.
For a multi-stage (cylinder) intermediate cooling compressor, when the segment (cylinder) non-cooling test is carried out, the cross section at the intake flange of each segment (cylinder) is the intake port.
For an intermediate gas-filling compressor, the cross section after the main airflow (segment outlet airflow before the gas-filling segment) and the gas-filling are mixed is the gas-filling segment intake port
Usually refers to the compressor outlet flange.
If a cooler belonging to the compressor is installed at the compressor outlet, the cooler outlet cross section is the compressor outlet.
When a multi-stage (cylinder) intermediate cooling compressor is carried out in the segment (cylinder) non-cooling test, the cross section at the outlet flange of each segment (cylinder) is the outlet.
Intermediate air extraction compressor uses the cross section of the outlet of the extraction section as the outlet. Compressor segment number
4 Test equipment and instruments
JB/T3165--- 1999
According to the different test systems (called test benches) connected to the compressor, it can be divided into two types of test benches: open and closed. 4.1 Open test bench
The open test bench uses air as the test gas, and is composed of a test pipeline, a flow measurement pipeline, and a throttle valve. According to the different connection methods between the test pipeline and the compressor inlet and outlet, it can be divided into three types of test devices: intake, outlet, and intake and outlet. 4.1.1 Intake test device (suitable for exhaust compressors): The test pipeline is connected to the compressor inlet end face, and the outlet end is open to the atmosphere (see Figure 1 and Figure 2).
If the air inlet of the compressor intake chamber shown in Figure 2 is horizontal, the test device should be arranged as shown in Figure 1. 4.1.2 Gas outlet test device (applicable to compressors supplying compressed gas): the inlet end face is open to the atmosphere, and the outlet end face is connected to the test pipeline (see Figures 3 and 4).
4.1.3 Gas inlet and outlet test device (applicable to single-stage or multi-stage compressors and intercooled compressor segmented test): the compressor inlet and outlet are connected to the test pipeline (see Figures 5 and 6). 4.2 Closed test bench
The closed test uses gases other than air as test gas, and consists of a test pipeline, a flow measurement pipeline, a connecting pipe, a throttle valve, a cooler and a gas supply device. It is divided into two types of test devices: single-channel and multi-channel closed. 4.2.1 Single-channel closed test device (see Figure 7): Applicable to single-stage or multi-stage uncooled compressor tests from single inlet to single outlet, and segmented tests of compressors with external intercooling. The device in Figure 7 can also be used when the compressor with an external intercooler is tested as a whole machine. If the performance parameters of the middle section need to be measured, the position of the measuring point shall be arranged according to the actual situation of the pipelines before and after the intercooler. 4.2.2 Multi-channel closed test device (see Figure 8 and Figure 9). 4.3 Test pipeline
The test pipeline shall adopt round tubes, and its size, shape and surface requirements shall comply with the following provisions. 4.3.1 The cross-sectional area of the inlet and outlet test pipelines shall be as close as possible to the area of the compressor inlet and outlet flange end faces. If they are different, a conical joint shall be used for connection.
4.3.1.1 The inlet test pipeline uses a convergent conical joint, and the ratio of the two cross-sectional areas shall not exceed 1.0~~1.3. 4.3.1.2 The outlet test pipeline uses a convergent or divergent joint, and the ratio of the two cross-sectional areas shall not exceed 0.7~1.3. 4.3.1.3 The external dimensions of the conical joint refer to the provisions in GB/T1236. 4.3.2 The inner wall of the inlet and outlet test pipelines shall be smooth and free of dust and peeling, and the length of the pipeline shall comply with the provisions of Figures 1 to 9 respectively.
4.3.3 The inlet and outlet test pipelines shall be provided with measuring holes for measuring static pressure and temperature respectively. 4.3.3.1 Holes for measuring static pressure: Drill 4 holes evenly distributed along the circumference on the same cross-section wall of the pipeline. The hole shall be perpendicular to the pipe wall, and the inner wall surface around the junction of the pipe and the hole shall be smooth and free of burrs to avoid blockage. According to the specific conditions of the gas, the diameter of the hole shall be as small as possible, and the maximum shall not exceed 3mm.
4.3.3.2 Holes for measuring temperature: Drill 4 holes evenly distributed along the circumferential direction on the same designated cross-section wall of the pipeline, and each hole is equidistant and staggered 45° from the hole for measuring static pressure.
4.3.4 When the dynamic pressure at the static pressure measurement point is greater than the pressure rise by 5%, 2 holes should be drilled at 90° intervals along the circumferential direction on the cross-section downstream of the static pressure hole for the installation of the dynamic pressure pipe.
4.4 Rectifier and porous plate
4.4.1 Rectifiers for regulating the air flow in pipelines are divided into two types: well-shaped and porous. The dimensions are specified in GB/T1236. 4.4.2 Perforated plate
The number of holes on a perforated plate shall not be less than 500/m, and the number of holes on the entire plate shall not be less than 50. The ratio of the total area of the holes to the cross-sectional area of the pipeline is determined by the following formula:
In the formula: An--total area of the openings of the perforated plate, m; Ap--twice the dynamic pressure of the pipeline.
JB/T3165-—1999
51DppAp
≥10D
JB/T 3165—1999
When measuring without a dynamic pressure tube, it is 10 Dz
JB/T 3165 -- 1999
≥12D2
JB/T 3165--19992.1 Single-circuit closed test device (see Figure 7): Suitable for testing single-stage or multi-stage uncooled compressors from single air intake to single air outlet, as well as segmented testing of compressors with external intercooling. The device in Figure 7 can also be used for whole-machine testing of compressors with external intercoolers. If it is necessary to measure the performance parameters of the intermediate section, the positions of the measuring points shall be arranged according to the actual conditions of the pipelines before and after the intercooler. 4.2.2 Multi-circuit closed test device (see Figures 8 and 9). 4.3 Test pipeline
The test pipeline shall adopt round tubes, and its size, shape and surface requirements shall comply with the following provisions. 4.3.1 The cross-sectional area of the inlet and outlet test pipelines shall be as close as possible to the area of the compressor inlet and outlet flange end faces. If they are different, a conical joint shall be used for connection.
4.3.1.1 The ratio of the two cross-sectional areas of the converging conical joint used in the inlet test pipeline shall not exceed 1.0~~1.3. 4.3.1.2 The ratio of the two cross-sectional areas of the converging or diverging joint used in the outlet test pipeline shall not exceed 0.7~1.3. 4.3.1.3 The external dimensions of the conical joint shall be as specified in GB/T1236. 4.3.2 The inner wall surface of the inlet and outlet test pipelines shall be flat, free of dust and peeling, and the pipeline length shall comply with the provisions of Figures 1 to 9 respectively.
4.3.3 The inlet and outlet test pipelines shall be provided with measuring holes for measuring static pressure and temperature respectively. 4.3.3.1 Holes for measuring static pressure: Drill 4 holes evenly distributed along the circumferential direction on the same cross-sectional wall of the pipeline. The hole shall be perpendicular to the pipe wall, and the inner wall surface around the junction of the pipe and the hole shall be smooth, free of burrs, and will not cause blockage. According to the specific conditions of the gas, the diameter of the hole should be as small as possible, and its maximum should not exceed 3mm.
4.3.3.2 Holes for measuring temperature: On the same specified cross-section wall of the pipeline, 4 holes are evenly drilled in the circumferential direction, and each hole is equidistant and staggered 45° from the hole for measuring static pressure.
4.3.4 When the dynamic pressure at the static pressure measurement point is greater than the pressure increase by 5%, 2 holes should be drilled at 90° intervals in the circumferential direction on the downstream section of the static pressure hole for the installation of the dynamic pressure pipe.
4.4 Rectifier and porous plate
4.4.1 Rectifiers used to adjust the airflow in the pipeline are divided into two types: well-shaped and porous. The external dimensions are specified in GB/T1236. 4.4.2 Perforated plate
The number of holes on a perforated plate shall not be less than 500/m, and the number of holes on the entire plate shall not be less than 50. The ratio of the total area of the holes to the cross-sectional area of the pipeline is determined by the following formula:
In the formula: An--total area of the openings of the perforated plate, m; Ap--twice the dynamic pressure of the pipeline.
JB/T3165-—1999
51DppAp
≥10D
JB/T 3165—1999
When measuring without a dynamic pressure tube, it is 10 Dz
JB/T 3165 -- 1999
≥12D2
JB/T 3165--19992.1 Single-circuit closed test device (see Figure 7): Suitable for testing single-stage or multi-stage uncooled compressors from single air intake to single air outlet, as well as segmented testing of compressors with external intercooling. The device in Figure 7 can also be used for whole-machine testing of compressors with external intercoolers. If it is necessary to measure the performance parameters of the intermediate section, the positions of the measuring points shall be arranged according to the actual conditions of the pipelines before and after the intercooler. 4.2.2 Multi-circuit closed test device (see Figures 8 and 9). 4.3 Test pipeline
The test pipeline shall adopt round tubes, and its size, shape and surface requirements shall comply with the following provisions. 4.3.1 The cross-sectional area of the inlet and outlet test pipelines shall be as close as possible to the area of the compressor inlet and outlet flange end faces. If they are different, a conical joint shall be used for connection.
4.3.1.1 The ratio of the two cross-sectional areas of the converging conical joint used in the inlet test pipeline shall not exceed 1.0~~1.3. 4.3.1.2 The ratio of the two cross-sectional areas of the converging or diverging joint used in the outlet test pipeline shall not exceed 0.7~1.3. 4.3.1.3 The external dimensions of the conical joint shall be as specified in GB/T1236. 4.3.2 The inner wall surface of the inlet and outlet test pipelines shall be flat, free of dust and peeling, and the pipeline length shall comply with the provisions of Figures 1 to 9 respectively.
4.3.3 The inlet and outlet test pipelines shall be provided with measuring holes for measuring static pressure and temperature respectively. 4.3.3.1 Holes for measuring static pressure: Drill 4 holes evenly distributed along the circumferential direction on the same cross-sectional wall of the pipeline. The hole shall be perpendicular to the pipe wall, and the inner wall surface around the junction of the pipe and the hole shall be smooth, free of burrs, and will not cause blockage. According to the specific conditions of the gas, the diameter of the hole should be as small as possible, and its maximum should not exceed 3mm.
4.3.3.2 Holes for measuring temperature: On the same specified cross-section wall of the pipeline, 4 holes are evenly drilled in the circumferential direction, and each hole is equidistant and staggered 45° from the hole for measuring static pressure.
4.3.4 When the dynamic pressure at the static pressure measurement point is greater than the pressure increase by 5%, 2 holes should be drilled at 90° intervals in the circumferential direction on the downstream section of the static pressure hole for the installation of the dynamic pressure pipe.
4.4 Rectifier and porous plate
4.4.1 Rectifiers used to adjust the airflow in the pipeline are divided into two types: well-shaped and porous. The external dimensions are specified in GB/T1236. 4.4.2 Perforated plate
The number of holes on a perforated plate shall not be less than 500/m, and the number of holes on the entire plate shall not be less than 50. The ratio of the total area of the holes to the cross-sectional area of the pipeline is determined by the following formula:
In the formula: An--total area of the openings of the perforated plate, m; Ap--twice the dynamic pressure of the pipeline.
JB/T3165-—1999
51DppAp
≥10D
JB/T 3165—1999
When measuring without a dynamic pressure tube, it is 10 Dz
JB/T 3165 -- 1999
≥12D2
JB/T 3165--1999
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