Some standard content:
Machinery Industry Standard of the People's Republic of China
General purpose axial flow compressor
This standard is equivalent to the international standard IS08011:1988 "Turbo Compressor for Process Industry 1 Subject Content and Scope of Application||tt ||JB/T4359—94
replaces JB4359--86
Design, Manufacturing Specifications and Data Sheets》.
This standard specifies the technical requirements for the design and manufacturing of general-purpose axial flow compressors (hereinafter referred to as compressors), and covers certain aspects of compressor driving devices, transmission equipment, lubrication and sealing oil systems, control instruments and auxiliary equipment. some requirements. This standard is applicable to axial flow compressors that transport air or other gases, and their energy head should be greater than 25000J/kg. For special-purpose axial flow compressors, it can also be used as a reference.
If there is any conflict between this standard and the contract or technical agreement, the provisions of the agreement shall prevail. 2 Reference standards
GB/T2888 Fan and Roots blower noise measurement method GB/T13306 label
JB3165 Centrifugal and axial flow blower compressor thermal performance test 3 general requirements
3.1 Gas properties
The calculation of gas properties should comply with JB3165 regulations. The user should explain to the supplier whether the gas is toxic, flammable or corrosive, and whether it contains solid impurities. 3.2 Inquiry
The user should describe the process requirements, flow regulation and any known abnormal conditions, and indicate which provisions of this standard are to be implemented. The user should indicate relevant design and safety specifications and any deviations from this standard. The user should specify the main spare parts that should be included in the quotation. 3.3 Quotation
The supplier should prepare a complete quotation to meet user requirements. Items not listed in the inquiry but deemed necessary by the supplier should be stated in the quotation. The supplier shall describe the flow regulation system of the compressor and its scope of supply. If not specified in the inquiry letter, the supplier may quote and supply the commonly used instruments listed in this standard. 3.4 Performance deviation
The compressor is tested according to JB3165.
For a fixed-speed compressor, the flow rate should be within the range of 0% to 15% of the specified value. Larger deviations are allowed for machines with small flow rates or for transporting certain gases (such as ammonia). The required specific power shall not exceed 4% of the specified value. The specific power required for variable speed compressors shall not exceed 4% of the specified value. In order to achieve the specified pressure and flow rate, the rotation speed can be changed. When the required speed exceeds nmax, the compressor operating speed range should be agreed upon between the user and the supplier. The required specific power refers to the input shaft power of the compressor per actual volumetric flow rate. The actual volume flow rate is the volume flow rate converted from the output flow rate to the inlet state.
The Ministry of Machinery Industry of the People's Republic of China approved the implementation on 1995-07-01 on 1994-07-01
401
.
JB/T4359-94
Input shaft power refers to the power required by the compressor shaft, excluding external transmission losses. External transmission (such as transmission) losses should be separately stated in the technical documentation.
3.5 Noise Control
3.5.1 If there are restrictions on the noise of the compressor and its auxiliary equipment, the user should explain it when making an inquiry. Noise technical conditions are proposed by users. The provider is not responsible for costs incurred due to incomplete requests made by users. 3.5.2 The maximum A sound power level allowed by the user from the compressor and its auxiliary equipment should be stated in the inquiry letter. The supplier should indicate the expected A sound power level of the main components supplied when quoting. 3.5.3 Noise measurement shall comply with the provisions of GB/T2888. If on-site noise testing is required, it can be agreed upon by both parties. Since the sound pressure level in the compressor room depends on the sound power emitted by the installed machine and the acoustic characteristics of the machine room, the supplier cannot provide the final sound level on site in advance.
3.5.4 In order to comply with the specified noise limits, the noise reduction measures that the supplier needs to take should be quoted separately. 3.5.5 If the user provides his own muffler, the supplier should provide the corresponding noise level information of the supplied equipment. 3.5.6 In the pipeline, mufflers and valves must be properly configured to avoid interference with each other under different operating conditions. This should be reached by mutual agreement between the supply and demand parties.
4 Compressors
4.1 General requirements
4.1.1 The design of compressors and auxiliary equipment should be considered for continuous operation at each specified operating point for at least three years. And consider starting, stopping and instantaneous surge conditions.
This is a design principle. It is undeniable that situations unexpected by the supplier will occur during continuous operation. 4.1.2 The number and layout of casings, including prime movers and auxiliary engines, should be agreed upon by both parties. 4.1.3 The structural design and layout of the compressor and auxiliary equipment should leave sufficient space for operation and maintenance. 4.1.4 The supplier should randomly provide various special tools and equipment required for installing components. The casing and bearing box should have centering pins, positioning keys, etc. to ensure accurate positioning when components are reassembled. To facilitate assembly and disassembly, lifting rings, hanging screws, jackscrews or similar components and guide rods should be provided. If a jackscrew is provided, care must be taken not to damage the sealing surface. For lifting eye screw holes, the thread type specifications should be printed next to them to avoid mistakes during use. 4.1.5 The design should take into account the ability to prevent moisture, dust and impurities from intruding into the adjusting mechanism, bearings and oil system during operation and parking. 4.1.6 The design of the compressor should comply with the climatic conditions of the installation location. Water accumulated in the casing components and pipes should be drained when the vehicle is stopped. Protective measures should be taken for parts that may malfunction or be damaged due to low temperatures. The supplier should explain the protective measures taken by the user, such as heating fault detection or heat insulation measures. The temperature of the lubricating oil and control oil supplied to people during driving should meet the requirements. 4.1.7 The welding and repair of the casing, pressure-bearing castings, and pipelines are usually the responsibility of the supplier and should comply with the supplier's corresponding specifications. 4.2 Chassis
4.2.1
Generally, the casing material can be selected according to the following principles: a.
For temperatures below -40C, the material should be used with the consent of both parties. Materials with higher impact toughness. For corrosive, toxic or flammable gases, users should specify special requirements when making inquiries. b.
Nodular cast iron can be used when the pressure is up to 6.4MPa. d.
When the pressure is up to 3.2MPa, gray cast iron can be used. e.
When the design pressure of the casing is above 6.4MPa, or the calculated maximum operating temperature of the casing is above 260C, steel parts should be used. Sealant is allowed on cast iron casing joints. 4.2.24
The internal stress relief treatment of steel welded casing should be carried out after welding 4.2.3
4.3 External force and external moment
402
JB/T4359—94
The supplier should explain the displacement of the casing joint due to thermal expansion, as well as the external force and external moment allowed to be exerted by the user on the casing joint. Under any specified operating conditions, including during shutdown, these external forces and moments must not affect the safe operation of the compressor, or destroy the alignment, change the assembly clearance, or generate excessive casing flange stress, etc. The pipeline supplier is responsible for arranging the pipelines and making calculations based on the displacement of the casing pipe and the allowable external forces and moments, and ensuring that the allowable values ??are not exceeded. The pipeline supplier should submit the arm channel calculation results to the supplier, but this does not relieve the pipeline supplier of its responsibilities. 4.4 Threaded connection
4.4.1 All threads should be metric threads and comply with relevant national standards. 4.4.2 Minimize screw holes and give priority to studs. The screw hole must not penetrate into the pressure chamber and the remaining wall thickness should be at least half the nominal diameter of the thread to prevent gas leakage.
4.4.3 Select the stud material for the casing according to the design temperature of the casing. When the temperature is -20 to +300°C, select grade 4.6 studs for the cast iron casing; select grade 5.6 studs for the cast casing. column. When the temperature exceeds the above range, the stud nut material used for corrosive media should comply with relevant national standards.
4.5 Diffuser and vane cylinder
Unless otherwise specified, the diffuser and vane cylinder can generally be made of cast iron. The diffuser channels should be free of any protrusions (such as casting irregularities).
4.6 Rotor
4.6.1 The fixation of each component on the rotor should ensure that it will not change its equilibrium state until the tripping speed at the maximum operating temperature. 4.6.2 The blades should ensure that resonance does not occur within the specified operating speed range, and the starting process and other possible transient states should be taken into consideration.
4.6.3 When selecting the rotor material, the supplier and the buyer should reach an agreement on the impact of the medium (for example, when containing H, S). 4.7 Labyrinth seal
4.7.1 There should be a device between the fixed part and the rotating part. There are labyrinth seals. The sealing disc can be installed on the fixed part or the rotating part. Seals should be easily replaceable. When the sealing disc is on the fixed part, a protective sleeve should be provided on the shaft. 4.7.2 The influence of gas composition and operating conditions should be considered when selecting sealing materials. 4.8 Balance plate and balance air pipe
4.8.1. The single-suction compressor is equipped with a balance plate with a balance tube to reduce the axial load of the stop bearing. 4.8.2 A labyrinth seal should be installed on the balance plate. 4.8.3 The balance pipe should be able to smoothly discharge the gas leaked from the balance plate seal, and its cross-sectional size should be larger than twice the balance plate seal gap so that the thrust does not exceed the rated load of the stop bearing.
4.9 Bearings and bearing boxes
4.9.1 The design of the bearing box should generally allow the bearings to be replaced without disassembling the horizontally split upper casing. 4.9.2 The bearing design should ensure a stable oil film under all specified working conditions including tripping speed. 4.9.3 The thrust bearing should be able to withstand bidirectional loads. It is best to adopt the tilting tile type in the main load direction. The thrust bearing should be sized to withstand the additional load transmitted from the outside through the coupling. When using a gear coupling, the minimum friction coefficient of 0.15 should be used to calculate the transmitted axial thrust. The supplier obtains the necessary data from the prime mover, transmission and coupling suppliers to determine the thrust bearing specifications. If it is necessary to start with axial load, the thrust bearing should be calculated accordingly. The compressor should be equipped with appropriate sensors to detect thrust changes or shaft displacement. 4.9.4 When designing the bearing box, consideration should be given to the installation of a vibration meter. At least a non-contact vibration probe can be installed near each bearing. 4.9.5 All bearings of the compressor must be compulsorily lubricated. Try to increase the flow area of ??the oil return pipe to reduce lubricating oil foam. When the compressed medium may affect the performance of the lubricating oil or bearing materials, the user should inform the supplier to take appropriate precautions. 4.10 Shaft seal
4.10.1 The type of seal should be agreed upon by both parties. The user should inform the supplier of any conditions of use that are not conducive to sealing. 4.10.2 During normal operation, dangerous and polluting gases must not leak into the atmosphere, but safe and reliable emission measures should be taken. 403
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4.10.3 The seal should be able to work reliably in running and parking conditions. The seal should be easy to remove and replace after installation. 4.11 Critical speed
4.11.1 Bending critical speed
The calculation of the bending critical speed should take into account the influence of external factors such as couplings, bearings and bearing boxes, and its value should comply with the requirements in Table 1. Table 1
Original
In the table: o
Hmin
rler
ler2
Motion
Machine||tt ||Rigid shaft
Flexible shaft
100% speed:
Minimum allowable speed;
The second critical speed;
The second critical speed Rotating speed.
Electric
Motion
Machine
ner ≥1. 2n100
ej≤0.85mmin
Perz1. 2no
Steam turbine or turboexpander
ner21.26nioo
er≤0.85nmin
ner2≥1. 26n10
If the process scope is large, the supply and demand parties can Negotiate another indicator to ensure reliable operation of the compressor. 4.11.2 Torsional critical speed
When the compressor is driven by a motor, the supplier usually only performs torsional vibration analysis. If the torsional natural frequency is within the excitation frequency range, the supplier should pay attention to the fact that no damaging stress occurs in the most loaded parts. Suppliers of motors, couplings and transmissions should provide relevant data to the supplier so that the supplier can carry out torsional vibration testing. analyze. 4.12 Vibration
4.12.1 Measurement method
Shaft vibration can be measured with a non-contact instrument near the radial bearing. The contact instrument can also be fixed on the bearing box to measure the vibration of the bearing box. 4.12.2 Allowable vibration levels
If specified at the time of inquiry, the vibration acceptance test can be carried out during the mechanical operation of the compressor, and the agreed-upon limit between the minimum allowable speed and the maximum continuous speed is not allowed to be exceeded. Vibration limits. The net shaft vibration can be found by subtracting from the shaft vibration reading the deviation caused by the mechanical out-of-roundness of the journal at the measuring position and the deviation caused by the magnetic unevenness of the shaft material at the measuring position. If non-contact probes are used, measurements should be made with two sensors on each bearing. The sensors are located at positions 80° to 100° apart from each other. If both supply and demand parties must specify allowable limits, they can be considered according to Figure 1. When determining the allowable shaft vibration amplitude of a machine, it should be noted that the shaft vibration amplitude is also different when the bearing structure is different. For example, elliptical pad bearings allow larger shaft amplitudes in the horizontal direction, while generally speaking, the allowable shaft amplitude of tilting pad bearings is smaller than the limit in the figure. If a contact vibrometer is used, the vibration frequency is measured in two vertical planes at 100% shaft speed. The effective value of its vibration speed shall not exceed 6.3mm/s.
4.12.3 Vibration monitoring
If the user requires vibration monitoring, the specific requirements should be stated in the contract in accordance with Article 4.12.2. 4.12.4 Alarm and trip values ??
Changes in amplitude and increase in amplitude may cause damage to the machine. Therefore, alarm and trip values ??can generally be controlled based on the values ??measured and recorded during the vibration acceptance test. It should not be controlled according to the limit value in Figure 1. The tripping value shall be specified by the supplier. 4.12.5 Moving characteristic diagram
It is recommended to prepare the vibration characteristic diagram of the compressor through frequency analysis when the machine is running at the normal operating point. Such diagrams can be used as an aid in identifying accidents while driving and later if problems arise. 404
4.13 balance
10
80
60
50
40
30
20
3×107
JB/T 4359-
94
5x10
10
100% shaft speed T||tt| |Figure 1 Allowable limit of shaft vibration amplitude
21
Through rotor assembly and balance correction, it should be basically free of internal couples and meet the allowable vibration magnitude requirements. Counterweighting should be done in at least two correction planes. Couplings and countershafts should be balanced individually. The half couplings are not corrected when the overall rotor is balanced. Do not use welding to counterweight.
4.14 Base
4.14.1 A base that is rigidly connected to the foundation (according to the requirements of the agreement) shall be provided for the compressor or compressor and transmission: the foundation shall be designed and constructed by the user in accordance with general specifications.
4.14.2 The surface on which the unit parts are placed on the base must be processed. In addition, it is allowed to use an adjustment pad or a multi-layer combination pad processed on both sides between the machine and the base:
4.14.3 In order to adjust the vertical position of the base on the foundation, a thread and pad should be provided randomly. 4.14.4 If necessary, grouting holes can be cast on the base, and the hole diameter shall not be less than 100mm. The holes should be positioned so that oil cannot accumulate on the exposed concrete floor.
4.15 Rotation direction arrows and signs
4.15.1 The direction of rotation should be agreed with the suppliers of the prime mover and transmission. The steering arrow should be cast on the compressor and transmission casing, or the steering arrow mark should be made of corrosion-resistant material and fixed on the compressor and transmission. 4.15.2
The compressor should have a product label made of corrosion-resistant materials, and its relevant requirements should comply with the regulations of GB/T13306. Its content may include:
a.
b.
c.
d.
e.
f.
g.
h.
i.| |tt||Manufacturer name;
Product number:
Product model:
Year and month of manufacture;
Import flow rate;
Design pressure ;
Design temperature:
Maximum continuous speed;
Jump speed.
When users have other requirements for signage content, they can inform the supplier for consideration. 405
5 Prime mover, transmission and coupling
5.1 Prime mover
JB/T 4359—94
.5.1.1 The type of prime mover is selected by the user . The power losses in the transmission or fluid coupling should be taken into account when determining the prime mover capacity. The output torque and starting torque of the prime mover should meet the compressor torque and speed requirements. When the properties and working conditions of the gas delivered by the compressor change, the power and speed of the prime mover may change accordingly. The supplier should inform the prime mover supplier of changes in this aspect in advance. If oil supply is provided in accordance with Article 7.1.1, the supplier shall be responsible for coordination. Noise control shall be in accordance with Article 3.5.
5.1.2 Steam turbine
Generally, the steam turbine as the main driving device should be designed according to the following conditions: a.Under normal steam intake and exhaust conditions, the steam turbine should be able to continuously supply 110% of the required power for each specified operating point and its corresponding speed.
b． For each operating point listed by the buyer in the inquiry, the steam turbine shall be able to continuously supply 100% of the required power under the minimum allowable continuous operation conditions of the minimum inlet steam and the maximum exhaust steam. C. The turbine should be able to operate continuously between the minimum and maximum continuous operating speeds of the compressor. 5.1.3 Motor
For each specified operating point and at its corresponding speed, the motor should be able to supply 115% of the required power of the compressor shaft, and the motor should be able to work continuously under this power.
The motor category and other design parameters shall comply with the contract provisions. The motor supplier should provide the supplier with necessary information for torsional vibration analysis. 5.1.4 Gas turbine
Gas turbine specifications shall be agreed upon by both supply and demand parties. 5.1.5 Turboexpander
If the turboexpander is specially used to drive a compressor, its power and rotational speed requirements are the same as those of a steam turbine. 5.1.6 Others
In other cases, the specifications and operating requirements of the prime mover shall be agreed upon by both parties. 5.2 Transmission
5.2.1 The parallel shaft gear corresponds to single helical teeth or herringbone teeth. Spur gears can be used in planetary gear transmission, and the tooth shape is determined by the supplier. 5.2.2 At the highest continuous speed of the compressor, the transmission should be able to transmit the torque value obtained by multiplying the rated torque by the corresponding service factor, and should be able to work continuously for at least 100,000 hours. The rated torque is the maximum torque at each specified operating point, which can be calculated according to the following formula: rated torque [N·m] ≥ 3000. Input power [kw] Input end speed [r/min]
Usually, the input power is equal to the design driving power. For transmissions that do not transmit the full drive power (such as couplings between housings), the input power needs to be calculated separately.
The recommended usage coefficients are shown in Table 2.
5.2.3 If a thrust bearing is used, it should be designed to withstand the auxiliary force transmitted by the coupling through friction and any gear axial meshing force. Please see item 4.9.3 for bearing specifications.
5.2.4 The rotating parts of the transmission should be subjected to a balance test and comply with the provisions of Article 4.13. 5.2.5 At the specified operating point, the critical bending speed of the low-speed shaft should not be within ±15% of the speed of the high-speed shaft. 406
Types of prime movers
The starting torque ratio of steam turbines, gas turbines, and turboexpander motors is not greater than 2
JB/T4359—94
Table 2||tt ||For synchronous motors, the ripple torque is less than 5 times the rated torque during starting and other transition phases.
relaxation
5.2.6 The performance requirements of lubricating oil should be agreed with the transmission supplier. Usage coefficient
1. 0--1. 2
1. 0~1.2
1.2~1.5
agreed with the transmission manufacturer
5.2.7 The direction of rotation of the shaft should be clearly marked. The steering arrow can be cast on the casing or made of corrosion-resistant material and fixed on the casing.
5.2.8 Noise control shall be in accordance with Article 3.5.
5.3 Couplings
5.3.1 Rigid or flexible couplings can be used between the compressor, transmission and prime mover. When the coupling speed exceeds 2000r/min, then The metal parts should be made of steel. 5.3.2 For the design torque and service life of the coupling, see 5.2.2. 5.3.3 The design of the coupling should enable the drive shaft to operate independently. 5.3.4 For gear couplings lubricated by oil injection, the formation of sludge in the coupling should be avoided. The filtration accuracy of lubricating oil should be agreed with the coupling supplier.
5.3.5 The coupling sleeve or intermediate shaft should be able to be removed without disassembling the compressor, transmission and motor in order to maintain the half coupling, bearings and shaft seals.
5.3.6 Who will supply the coupling between the prime mover and the compressor, conduct the balancing test and install it should be agreed in advance by both parties. 5.3.7 The coupling pin should be weighed and matched so that it can be replaced without affecting the balance. 5.3.8 The end of the spindle that is not integrally forged can be cylindrical or conical and interference-fitted with the coupling. When using keys on the shaft, double keys should be arranged symmetrically to facilitate balance and replacement. 5.3.9 The coupling guard should be set up to facilitate inspection and disassembly. If the coupling has lubricating oil entering and exiting the pipeline, it should comply with the provisions of Article 6.6. 5.3.10 The supplier should clarify whether to limit the axial clearance of the coupling. 6 Auxiliary equipment
6.1
． General requirements
6.1.1 For auxiliary equipment belonging to the pressure vessel category, if the user does not request it, the supplier shall design, manufacture, inspect and test it in accordance with the relevant general specifications.
6.1.2 When casings made of carbon steel in auxiliary equipment come into contact with water or other corrosive media, the wall thickness should have a corrosion margin of at least 3mm.
6.2 Gas Cooler
6.2.1 The cooling water side of the gas cooler should be designed according to the water pressure specified by the user, but it should be designed at least according to 0.6MPa gauge pressure or vacuum.
Under special circumstances (for example, the medium is chlorine) the water pressure is allowed to be lower than the air pressure. 6.2.2 The fouling coefficients of the water side and the gas side should be agreed upon by both parties. If not specified, the water side fouling coefficient may take the value in Table 3. 6.2.3 If water flows in the pipe, its minimum flow speed should be maintained at 1m/s. Table 3
Water
Closed cycle (purified water)
General cooling tower water
Salt water
Fouling coefficient.m2·K/W|| tt||0. 85 ×10-4
1.7X10
3.4X10*
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6.3 muffler
JB/T4359—94|| tt||When designing the muffler, the worst working conditions such as compressor surge, maximum flow, maximum pressure, temperature and medium corrosiveness should be taken into consideration.
6.4, general requirements for pipelines
6.4.1 The specifications of pipes should comply with relevant national standards and avoid non-preferred specifications. 6.4.2 The scope of supply of pipelines shall be agreed upon by both parties. 6.4.3 The stop valve at the supply limit is not a normal supply part of the supplier. 6.4.4 The flange at the supply limit shall be provided by the supplier under the following circumstances: when proposed by the user;
a.
b, when the flange does not meet the standards proposed by the user or relevant national standards. 6.4.5 The supplier shall provide the couplings and fasteners required for equipment connection, including fasteners for flanges at the supply boundary. 6.4.6 The drainage joint valve, blind plate and screw plug at the lowest point should be provided by the hip channel supplier. The exhaust valve at the highest point of the water pipeline shall be provided by the pipeline supplier.
6.4.7 The supplier should accurately determine the location, size and type of the end of the equipment pipeline. 6.4.8 Except for instrument air pipelines, sleeve-type pipe joints are generally not allowed to be used. 6.4.9 Pipes that may be used as supports during maintenance or other operations should be strong enough or well supported, or the pipeline supplier should provide protective measures.
6.4.10 Each pipeline and auxiliary equipment provided by the supplier that is part of the device should be supported by the supplier to minimize the possibility of damage caused by factors such as vibration, thermal expansion, and self-weight. 6.4.11 When the supplier provides external pipelines of the device (if the pipeline cannot be supported by the unit or its base) without providing brackets, the supplier should provide the user with suggestions for arranging brackets.
6.4.12 The supplier uses flexible joints to reduce stress and buffer thermal expansion, and should negotiate with the user to resolve installation and support issues. 6.4.13 The pipeline should be free of rust, slag, weld flash and other foreign matter. 6.5 Process gas pipeline
6.5.1 The inner diameter of the process gas pipeline shall not be less than 20mm. 6.5.2
Under normal circumstances, the pipelines installed by the user shall not impose load on the supplier's equipment. 6.5.3 If the process gas is explosive or otherwise hazardous, the stop valves on the cleaning joint and exhaust joint should be able to prevent accidental operation. 6.6 Auxiliary pipelines
6.6.1
The auxiliary pipelines include the pipelines of the following systems: a.
b.
.
Lubricating oil, control oil, sealing oil:
Sealing air, balancing air: www.bzxz.net
Cooling water;
Exhaust, drainage, ventilation; ||tt| |d
e.
Instrumentation, buffering, measurement.
6.6.2 Generally, carbon steel seamless pipes are used for gas pipelines and oil pipes; seam-welded pipes can be used for water pipes; stainless steel pipes are recommended between lubricating oil, sealing oil filters and machines.
6.6.3 If the user agrees, the measuring pipe and buffer pipe can be copper pipe or plastic pipe. 6.6.4 The minimum rated pressure of all pipe joints is 1.0MPa. 6.6.5. The horizontal pipe of the oil return pipeline should have a slope of 1:25 leading to the fuel tank. 6.6.6 Except for the discharge pipe from the instrument or control device, the inner diameter shall not be less than 20mm. The user should arrange the exhaust system so that the process gas can be removed reliably.
6.6.7 Piping systems are best made by bending and welding. In addition to instrument joints, seal welding should be used for pipe joints for flammable, toxic or corrosive media.
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6.6.8 Oil pipelines made of carbon steel must be pickled and passivated. 7 Lubricating oil and sealing oil systems
7.1 General requirements
7.1.1-Generally, lubricating oil and sealing oil systems are provided by the supplier. Lubrication, sealing, and control oil systems can be combined. Its oil supply object is:
a. Bearings for compressors, transmissions and prime movers; compressor seals;
b.
couplings;
c.
d, compressors and prime movers control system and jumper system. 7.1.2 Filters and coolers should have drain and exhaust ports with valves. These valves serve to vent, purge, fill and overflow during compressor operation. The diameter of the valve shall not be less than 12mm. 7.2 Oil tank
7.2.1 The oil tank is best separated from the compressor. The oil tank should be internally derusted. It is recommended to take anti-rust measures other than painting. Tanks with equipment on top should be rigid enough to prevent dents and vibrations. 7.2.2 All openings on the cover plate should be equipped with sealing gaskets and should be at least 25mm higher than the upper surface to prevent solid particles or water from entering. 7.2.3 There should be an opening with an inner diameter of at least 500mm on the cover plate to facilitate inspection and cleaning of the inside of the fuel tank. The bottom plate of the fuel tank should be tilted + and a drain outlet should be arranged at the lowest point so that all oil can be drained. Deflectors should be used to prevent air bubbles and impurities from being entrained in the lubricating return oil. 7.2.4 There should be an oil level gauge with continuous indication, and there should be marking lines for the maximum oil filling amount, maximum and minimum working oil levels. The oil level gauge shall be suitable for field installation and shall be sheathed. The fuel tank should have an oil filling hole with a screen and ventilation, but it should be kept away from dirt. 7.2.5 The size of the fuel tank shall be determined according to the following requirements: a. At the lowest working oil level, there should be 8 minutes of normal oil content in the tank. b. There should be 5 minutes of normal oil volume between the lowest working oil level and the pump cavitation oil level. The above normal oil quantity refers to the oil return quantity at the normal operating point of the compressor. 7.2.6 If there is an oil heater, its power should be enough to raise the oil temperature to the minimum operating temperature required by the supplier within 12 hours. However, its power density shall not be greater than 20kW/m2.
If a steam heater is used, the working oil must not be in direct contact with the steam pipe. If an immersed electric heater is used, it must have constant temperature control, and its heat density must not cause the lubricating oil to deteriorate. When the oil level above the heater is lower than 50mm, the power supply should be automatically cut off and heating stopped. 7.3 Pumps and their drivers
7.3.1 Each oil system must have at least one main oil pump and... one backup oil pump. 7.3.2 The capacity of the two pump drivers and the entire oil system should be sufficient for the two pumps to operate continuously in parallel. 7.3.3
The main oil pump can be driven alone or driven by the main shaft. If the main oil pump driven by the spindle reverses, it should not stop working and still maintain sufficient oil volume to prevent machine damage. 7.3.4
7.3.5
The standby oil pump should be designed to be independently driven to supply oil. When the oil pressure drops below a safe value, the backup oil pump should be able to start automatically to ensure oil supply and keep the machine running. If the backup oil record 7.3.6
is driven by a steam turbine or there is an agreement between the supply and demand parties, an accumulator or high-level oil tank should be equipped to maintain the lubricating oil pressure during the boosting period of the backup pump. A pressure switch (pressure relay) with a shut-off valve and a throttle should be provided to check the proper functioning of the backup oil pump during normal operation.
7.3.7 Positive displacement pumps shall be equipped with an externally mounted full-flow safety valve and a return pipe leading to the tank. The opening pressure of the safety valve should be adjusted to a position that exceeds 10% of the maximum pressure, taking into account the drive of the variable speed pump and the performance of the pressure regulating valve. 7.3.8 When the pump is driven by the main shaft, the check valve of the pressure pipe should have an appropriate starting oil filling function so that oil can be pumped up when the compressor is started.
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