Some standard content:
Machinery Industry Standard of the People's Republic of China
Centrifugal Pressure
Compressor
1 Subject Content and Scope of Application
JB/T 6443-92
This standard stipulates It covers the basic technical requirements, inspection and testing, marking, packaging, transportation and storage of centrifugal compressors and their auxiliary equipment.
This standard applies to centrifugal compressors transporting air or other gases. This standard does not apply to blowers or ventilators with gas pressure lower than 34kPa. This standard does not apply to the "integrated gear speed-increasing assembled centrifugal compressor for instrument air in general refineries" referred to in JB4113. Note: For the clauses marked with · before the clauses of this standard, the relevant content shall be determined by the buyer. These determinations are filled directly on the data sheet prepared by the Party [see Appendix A (Supplement), otherwise, it should be indicated in the quotation or order contract. The seller can provide alternative designs (see Article 7.1.1.13 for a list of differences). Equivalent inch sizes, fasteners and flanges can also be used after the buyer and seller agree. When the standards conflict with the ordering contract, the provisions of the ordering contract shall prevail. 2 Reference standard
GB150| |tt||GB196
GB197
GB 699
GB 1220
GB1226
GB1348
GB3077
GB3323| |tt||Steel pressure vesselsbzxZ.net
Basic dimensions of ordinary threads
Tolerances and fits of ordinary threads
Technical conditions for high-quality carbon structural steel
Stainless steel rods||tt| |-General pressure gauge
Nodular iron castings
Technical conditions for alloy structural steel
Radiography and quality classification of steel melted welded joints GB 4216.1
GB 4216.2||tt| |Gray cast iron pipe flange nominal pressure, test pressure and working pressure 2.5 bar gray cast iron pipe flange dimensions
6 bar gray cast iron pipe flange dimensions
GB 4216. 3 6
GB4216.410 bar gray cast iron pipe flange size GB4216.516 bar gray cast iron pipe flange size GB 4216.6
25 bar gray cast iron pipe flange size
GB 4216.7
2.5 and 6 Size of gray cast iron threaded pipe flange GB4216.810 and size of 16 bar gray cast iron threaded pipe flange GB 4216. 9
Asbestos rubber gasket size for gray cast iron pipe flange GB 4216.10
Gray cast iron Technical requirements for arm flange and gasket
GB4457~GB4460 Mechanical Drawing
GB6654
Carbon steel and low alloy steel thick steel plates for pressure vessels Ministry of Mechanical and Electronics Industry of the People's Republic of China 1992-07 -20 Approved 416
Implemented on 1993-01-01
GB7306 Pipe threads with thread seals
GB7307 Pipe threads without thread seals
JB/T 6443-- 92
GB8542 Turbine gear transmission technical conditions GB9112~~GB9131 (except GB9127) Steel arm flange and gasket GB9439 Gray iron castings
GB9444
Magnetic particle flaw detection of steel castings and its quality rating method GB12380.6PN5.OMPa (50bar) convex overall ductile iron pipe flange GB12384
GBI 236
JB1152
JB2977
JB3165||tt| |JB3964
JB3965
JB4113
JB4365
HGJ 21
Ductile iron flange technical conditions
Field equipment industrial pipeline welding engineering construction And acceptance specifications for boilers and steel pressure vessels butt joint ultrasonic flaw detection Fan and Roots blower terminology
Centrifugal and axial flow blower compressor thermal performance test pressure vessel welding process qualification
Steel pressure vessel Magnetic particle inspection
Integral gear speed increase for general oil refining and instrument air, lubricating and sealed regulating oil system for assembled centrifugal compressor fans
Chemical enterprise explosion and fire hazard environment power design specification ZBK54030 industrial steam turbine Use flexible coupling 3 terms
The terms used in this standard are defined in 3.1~3.21 (see Figure 1). 417
Specified operating point
A
JB/T 6443- -92
The lowest 1st critical speed·shaft
The lowest 2nd critical speed Sou
Tripping speed·Steam turbine
Yaozha speed gas turbine
Most continuous speed
300% speed
Normal speed
D
B
Dish,
-Operating speed
Minimum operating speed
Single-shaft gas turbine
Minimum operating speed||tt ||Steam turbines and twin-shaft gas turbines
Maximum critical speed
mulberry shaft
126%
105%×1.2
115.5%105% ×1.1
110. 3%=105%×1. 05
Compressor rated operating point
105%100%×1.05
Normal operating point||tt ||98% (setting)
Specify operating point
(88%=98%×0. 9)
(78%=98%×0.8)||tt| |1
66. 3%=78%×0.85
Stability
Adjustability
Figure 1 Terminology diagram
Note: (D except In addition to the relationships expressed by specified numbers, the relative dimensions shown in this figure are for illustration only. The inlet flow
②The energy head required by point A at 100% rotation speed and the compressor are designed to meet all specified operating points. (such as point C). ③The energy head-flow curve at 100% speed extends to 115% of the flow rate at point D, and the energy head-flow curve at other speeds should extend to 115% of the corresponding flow rate at each speed. For example: the energy head-flow curve at 105% rotational speed should extend to a flow rate that is 1.05×1.15 times the flow rate at point D; the energy head-flow rate curve at 90% rotational speed should extend to a flow rate that is 0.9×1.15 times the flow rate at point D, etc. etc. These points form an approximate flow limit line.
3.1 Normal operating point: The seller should generally ensure that the performance of this operating point is within the deviation range specified in this standard. .
3.2 Normal speed (1/min): the speed corresponding to the normal operating point. 3.3100% speed (r/min): higher than the normal speed and the highest speed among all specified operating points. Speed. If there is no operating point higher than the normal speed, the 100% speed is the normal speed. For a motor-driven compressor, the 100% speed should be equal to the gear ratio (if there is a speed increaser) multiplied by the equipped motor. Speed ??at full load. 3.4 Rated operating point: a specific point on the 100% speed line, the flow rate at this point is equal to the maximum flow rate among all specified operating points. 3.5 Maximum continuous speed (r/min): for variable speed drives. For compressors, the speed should be at least equal to 105% of the 100% speed. For a compressor driven by a constant speed machine, this speed should be equal to 100% speed, which is equal to the normal speed. 3.6 Minimum allowable speed (r/min): The lowest continuous operating speed allowed by the manufacturer's design. 3.7 Jump speed (r/min): the speed when the emergency overspeed safety device forces the driver to stop (see Table 1). 418
Driver type
Steam turbine
Gas turbine
Variable speed motor
Constant speed motor
Reciprocating engine
JB/T6443--92
Table 1
Tripping speed of driver
Tripping speed (percentage of maximum continuous speed) 115
110
105
110
100
110
Note: When using 115, the user should specify or stipulate in the contract the accuracy of the turbine speed regulation. 3.8 Stability (%): At rated operating speed, the percentage of the difference between rated flow and surge point flow to rated flow. 3.9 Adjustability (%): When the compressor unit operates under the rated inlet temperature and gas composition conditions, the percentage of the difference between the rated flow rate on the rated energy head line and the surge point flow rate to the rated flow rate. 3.10 Maximum allowable temperature: the maximum continuous operating temperature designed by the manufacturer for the equipment (or any parts or components). 3.11 Maximum sealing pressure: The highest pressure expected at the seal under specified static or operating conditions, and during startup or parking. 3.12 Maximum allowable working pressure: The maximum continuous working pressure designed by the manufacturer for the equipment (or any parts or components) at the maximum allowable temperature.
3.13 Horizontal split: The joint surface of the casing is parallel to the center line of the shaft. 3.14 Vertical split: The joint surface of the casing is perpendicular to the center line of the shaft. 3.15 Alarm point: refers to the set value of a certain parameter. When the parameter reaches this value, an alarm will be automatically issued to indicate that a certain operating condition needs to be corrected.
3.16 Parking point: The setting value of a certain parameter, under which the system will need to park automatically or manually. 3.17 Retention pressure: The pressure of the compressor system when the compressor is stopped. 3.18 Inlet volume flow rate (m2/h): The flow rate determined under suction conditions such as pressure, temperature, compressibility, humidity and gas composition at the compressor inlet flange.
3.19 Actual volumetric flow rate (m2/h): The flow rate in a state determined by temperature, pressure and other conditions on any given section. Since this term describes the flow at many locations, the actual volume flow rate cannot be used interchangeably with the inlet volume flow rate. 3.20 Standard volume flow rate [m/h (N)]: Convert the pressure measured at any cross-section to 0.1014MPa (A ), the corresponding volumetric flow rate when the temperature is converted to 15.56°C and the compressibility coefficient is 1.0 in the dry gas state. Note: (A) in this standard represents absolute pressure, and (N) represents standard status. 3.21 Design: The use of the word "design" in any term (such as design power, design pressure, design temperature, design speed) should be avoided in the buyer's technical conditions. This term applies only to designers and manufacturers of compressors. 4 Technical Requirements - Basic design of compressors and auxiliary equipment 4.1 General
4.1.1 The design and composition of the compressors and auxiliary equipment described in this standard should ensure that their service life is at least 20 years; uninterrupted Operation time is at least 3 years. This is a generally accepted design rule. 4.1.2 Unless otherwise specified, the outlet energy head and flow design of the compressor at the normal operating point shall not have negative deviations. Under the above conditions, its power shall not be greater than 104% of the design value at the normal operating point. See the optional performance test provisions in 5.3.6.1.1. 4.1.3 The continuous rise of the energy head-flow characteristic curve from the rated point to the expected surge point. When the flow rate is more than 10% of the surge flow rate specified in the quotation, the compressor should be able to operate continuously when the bypass path is not opened. 4.1.4 Unless otherwise specified, the cooling water system should be designed according to the following conditions: flow rate through the heat exchange surface 1.5~2.5m/s
419
maximum allowable working pressure ≥0.52||tt| |Test pressure
Maximum pressure drop
Maximum inlet temperature
Maximum outlet temperature
Maximum temperature rise
Minimum temperature rise
Water side Fouling coefficient
Shell side corrosion margin
≥0.79
0.1
32
49
17
11| |tt||0.35
3.2
JB/T 6443--92
MPa(G)
MPa(G)
MPa||tt ||C
℃
C
C
m2·K/kw
mm
The cooling water system should be equipped with complete Bleed and drain facilities. Note: ① If the minimum temperature rise regulations conflict with the flow rate regulations on the heat exchange surface, the seller should notify the buyer. The flow rate of the heat exchange surface is stipulated to minimize the fouling on the water side wall; the minimum temperature rise is stipulated to minimize the amount of cooling water. The final selection should be decided by the buyer. ②) In this standard (G) indicates gauge pressure.
4.1.5 The equipment layout including piping and auxiliary equipment shall be designed jointly by the buyer and the seller. Equipment layout should leave sufficient separation space and safe passage for operation and maintenance.
4.1.6 All equipment should be designed to allow easy and economical maintenance. The structure of major components such as casings and bearing housings should be designed (e.g. provided with bosses or locating pins) and manufactured to ensure precise alignment during reassembly. 4.1.7 The inner casing of a vertically split cylindrical compressor should be designed to be easily extracted from the outer casing and easily disassembled for inspection and replacement of parts.
4.1.8 The buyer should indicate whether the equipment is installed indoors (with or without heating) or outdoors (with or without a roof cover), as well as the climate and environmental conditions of the place where the equipment is working (including the highest and lowest temperatures, abnormal humidity or dust, etc. ). The unit and auxiliary equipment should be suitable for operation under these special conditions. In order to guide users, the seller should list in the quotation the special protection measures required by the buyer. If specified, the seller shall take measures for the unit.
4.1.9 The equipment provided by the seller shall comply with the maximum allowable sound pressure level specified by the buyer and seller. Control of noise sound pressure levels for all equipment provided shall be an effort by the buyer and seller to comply with applicable local standards and regulations for environmental noise limits. 4.1.10 The buyer should put forward special requirements regarding fluid injection to the seller in the inquiry letter. 4.1.11 Equipment should be designed to operate at tripping speed and maximum allowable working pressure without damage. The performance of the machine and its driver, as shown on the test bench and on a permanent basis, shall be within the limits specified in the standard. The performance of the entire 4.1.12
unit after installation shall be the sole responsibility of the buyer and seller. 4.1.13 Many factors (such as pipe loads, alignment under operating conditions, support structures, handling during shipment and on-site handling and assembly) can adversely affect on-site performance. In order to minimize the impact of these factors, the seller shall review and evaluate the buyer's piping and foundation drawings; if specified, the seller's representative shall: a.
Observe disassembling flanges and inspect the piping;||tt ||b.
Check alignment at operating temperature;
.
4. 1. 14
Be present for inspection at initial alignment time.
●Motors, electrical components and electrical devices shall be suitable for the regional classification (grade, group and category) specified by the buyer on the data sheet, and shall comply with the relevant requirements of HG]21, and the actual regulations are and regulations provided. 4.1.15 Spare parts of compressors and auxiliary equipment should meet all provisions of this standard. 6 If specified, the compressor and compressor unit should be able to use air for on-site testing. Its performance parameters and precautions to be taken shall be 4. 1. 16
negotiated between the actual party and the seller.
4.1.17 The names of the main components of the centrifugal compressor are shown in Appendix H (reference parts). 4.2 Chassis, partitions and inlet guide vanes
4.2.1 The thickness of the casing shall be suitable for the maximum allowable working pressure and test pressure, and shall have a corrosion margin of at least 3.2mm. The circumferential 420
.
JB/T 6443..92
axial stress value of the casing design should refer to the principles of Appendix F (reference parts) to determine the selection at the highest operating temperature. The maximum allowable tensile stress value of the material. 4.2.2 The feet and adjusting bolts should have sufficient rigidity to enable the machine to be moved with transverse and axial jackscrews. 4.2.3 The maximum allowable working pressure of the casing should be at least equal to the setting value of the safety valve; if the setting value of the safety valve is not specified, the maximum allowable working pressure should be at least 1.25 times the specified maximum exhaust pressure (G). System protection devices will be provided by the purchaser. 4.2.4 Unless explicitly requested by the buyer, the casing is not allowed to be designed as a pressure-rated casing. With the consent of the buyer, the seller may design the casing to be pressure-rated, but shall specify the pressure limits of each part of the casing and the maximum allowable working pressure. 4.2.5 The horizontally split casing should have sufficient rigidity so that when the upper half of the casing is disassembled and assembled, the running clearance and bearing alignment between the rotor and casing will not be affected.
4.2.6 Under the following conditions, the casing should be made of steel materials: air or non-flammable gas when the maximum allowed working pressure exceeds 2.76MPa (G): a.
b. Air or non-combustible gas when the calculated maximum outlet temperature at any operating point exceeds 260°C at the maximum continuous speed and allowable operating range (the maximum temperature is usually near the surge point); c.
combustible gas or Toxic gas.
4.2.7 In addition to the operating conditions specified in 4.2.6, the casing may be made of cast iron or other materials. 4.2.8 Unless otherwise specified, when the hydrogen partial pressure (at the maximum allowable working pressure) exceeds 1.When 38MPa (G), the casing should be a vertically split structure.
Note: The partial pressure of hydrogen is calculated by multiplying the specified maximum mole (volume) percentage by the maximum allowable working pressure. 4.2.9 Horizontally split casings should use metal-to-metal bonding surfaces (appropriate sealant should be added between the bonding surfaces) and tightened with appropriate bolts. Gaskets (including strips) should not be used to connect the horizontally split mid-planes. Gasket). With the buyer's consent, the connection between the horizontally split casing can be processed into an annular groove on the middle surface and sealed with a (ring). In the vertically split casing, when the end cover and the cylinder When there is a gasket connection, the gasket should be limited and reliably protected. The gasket material should be suitable for all specified use conditions. 4.2.10 To facilitate disassembly and reassembly, jackscrews, guide rods and casings should be provided. Locating pin. When using a jackscrew to separate the joint surface, a groove should be machined on the flange surface that bears the jackscrew to prevent leakage or poor fit on the joint surface. The guide rod should be of sufficient length to prevent the casing from being damaged when loading and unloading. Damage to the internal components and studs on the casing. The lifting eye or eyebolt device is used to lift the upper casing. The lifting method of the complete machine after assembly shall be specified by the seller
4.2.1. When drilling or processing screw holes on the pressure-bearing surface of the casing, the hole diameter should be minimized. In order to prevent leakage on the pressure-bearing surface of the casing, the thickness around the light or screw hole and at the bottom of the hole should be at least equal to half the nominal diameter of the bolt and The sum of the corrosion allowance (3.2mm). 4.2.12 It is not allowed to use filler in the gap between the stud and the hole to prevent leakage. 4.2.13 The surface roughness R value of the finished mounting surface of the compressor should be 3.2~~. 6.3μm. The fastening or foundation bolt holes should be perpendicular to the mounting surface and should be flat.
4.2.14 The optimal depth of the blind screw hole is the diameter of the stud. 1.5 times. Both ends of the studs should be chamfered, and their length should be 1.5 times the thread pitch.
4.2.15 Internal and external bolt connections shall comply with the detailed provisions of 4.2.15.1~4.2.15.1. Provisions of GB196 and GB197. 4.2.15.2 Studs should be used instead of bolts. 4.2.15.3 When connecting externally, sufficient wrench space should be left around the bolts (columns) to allow the use of a set wrench or a box wrench. 4.2. .15.4 Unless otherwise formally required by the purchaser, hexagon socket head bolts, slotted nuts or hand nut type bolts shall not be used for external connections
Class 5 partition plates and inlet guide vanes shall be suitable for all specified operations. conditions, as well as starting, stopping, jumping, returning to stability and instantaneous vibration. 4.2.16 | The seller should determine the maximum pressure difference that the partition provided can accommodate
4.2.17 Internal connections should be designed to minimize leakage and be easy to disassemble. 4.2.18 In order to minimize internal leakage, all connections must be made. Replaceable labyrinth seals shall be provided at extremely small internal gaps. When the buyer does not require 421
.
JB/T6443-92
, the labyrinth seal shall be stationary and easily replaceable. Structure. 4.2.19 If not specified by the buyer, the partition shall be designed as a horizontally split structure. The partition should be provided with lifting eye screw holes or other lifting measures to facilitate disassembly.
4.2.20 If the partitions are required to be cooled, the upper and lower partitions of the horizontal split should have independent cooling channels. The inlet and outlet of each coolant channel should be connected to headers at the top and bottom of each casing respectively. 4.3 Casing connections
4.3.1 General
4.3.1.1 All process gas connections on the casing shall be suitable for the maximum allowable working pressure of the casing specified in 4.2.3. 4.3.1.2 All takeovers by the Buyer shall be accessible for maintenance without moving the machine. 4.3.1.3 Joints, pipelines, valves and accessories with nominal diameters of DN32, 65, 90 and 125mm should not be used. 4.3.1.4 The connectors welded to the casing should meet the material requirements of the casing (including impact value), not the requirements of the connecting pipe material. 4.3.1.5 The welding of all nozzles should be completed before the hydraulic test (see 5.3.2). 4.3.2 Main process flow connectors
4.3.2.1 The inlet and outlet connections should be flange connections or stud connections after processing the plane. The orientation of the pipe mouth should be as specified in the data sheet. The simple compressor inlet and outlet pipes should be arranged on the outer casing, not on the end cover. For the vertical part cantilever compressor, the process gas inlet pipe can be arranged on the end cover.
4.3.2.2 Gray cast iron flanges and gaskets shall comply with the regulations of GB4216.1~GB4216.10; steel pipe flanges shall comply with the regulations of GB9112~GB9131 (excluding GB9127). Steel flanges larger than the nominal diameter DN600mm shall comply with the large-diameter carbon steel flange standards agreed upon by both parties.
4.3.2.2.1 Raised integral flanges are not allowed on cast iron casings. 4.3.2.2.2 Steel flange standards that are thicker and have a higher outer diameter than the above are allowed. 4.3.2.3 When using connectors different from the above steel flange standards, the buyer's consent is required. If specified, the seller shall provide all mating flanges and matching studs and nuts.
4.3.2.4 Cast iron flanges equal to or smaller than the nominal diameter DN200mm shall be flat flanges, and their minimum thickness shall comply with the thickness corresponding to GB12380.6 (PN5MPa).
4.3.2.5 The center circle of the bolt hole of the casing flange and the inner diameter of the flange should have certain coaxiality requirements, so that the annular area of ??the processed sealing convex (concave) platform can accommodate a complete Standard gasket without extending the gasket into the fluid. 4.3.2.6． All flanges and pipes should comply with the relevant regulations in GB4216.10, GB12384 and GB9125. Such as: selection of materials and surface roughness, etc.
4.3.3 Auxiliary connecting pipes
4.3.3.1 Auxiliary connecting pipes shall include but are not limited to the following pipes: ventilation, liquid injection, sewage discharge (see 4.3.3.2), cooling water, lubrication and Connections for sealing oil, flushing, buffer gas and balance plate cavity. 4.3.3.2 For horizontally split casings, the seller should provide all gas channel exhaust interfaces; for vertically split casings, the exhaust interfaces should be set at the lowest point of each inlet section, the lowest point between the inner and outer casings, and at each exhaust the lowest point of the segment. If specified, separate drains should be provided at each stage, including the balance plate cavity.
4.3.3.3 The flange shall comply with the regulations of GB9113~GB9131 (except GB9127). 4.3.3.4 The auxiliary pipe shall have a nominal diameter of at least DN20mm (see Article 4.3.1.3), and shall adopt socket welded flange connection or processed stud connection. For socket welding structures, there should be a 1.5mm gap between the pipe end and the bottom of the socket hole of the chassis before welding. 4.3.3.5 When the flange connection of socket welding cannot be used or the open structure can be connected with studs after processing, an interface with a nominal diameter of DN20~40mm can be used with the consent of the buyer. Threaded connection can be used, and the threaded interface should be set according to the provisions of 4.3.3.5.1~~4.3.3.5.3. 4.3.3.5.1 The screw holes and bosses of pipe threads shall comply with the relevant provisions of GB7306. 4.3.3.5.2 The pipe thread shall comply with the standard part of GB7306 tapered thread. 4.3.3.5.3 Threaded joints should be sealed welded. However, in cast iron equipment and instrument joints and other places that need to be frequently disassembled during maintenance, 422
JB/T6443-92
is not allowed. Sealing welding. Sealing welding should comply with relevant regulations such as GBI236. 4.3.3.6 Threads, pipe threads and inserted parts should preferably not exceed 150mm in length and should be installed in the opening holes of threaded connections or socket welds. See Table 2 for the minimum wall thickness of threaded pipe joints and insert welding. Each pipe joint shall be equipped with a butt welding flange, socket welding flange or ring loose flange. Table 2
Nominal diameter of pipe
DN
20
25
40
Minimum wall thickness of threaded pipe joint||tt| |5
5.5
7
mm
Minimum wall thickness of welded pipe joints
4
4
5 | The recommended value for the ratio of thread length to diameter is 0.6~~0.45, and the smaller value is used when the thread diameter is small. These screw plugs should meet the requirements of the chassis material. The screw plugs that need to be removed should be made of corrosion-resistant materials. Threads should be lubricated. Sealing tape should not be used on the threads of plugs used in oil lines. Plastic screw plugs are not allowed.
4.4 External forces and external moments
4.4.1 Each nozzle of the compressor should be designed to withstand the external force and external moment calculated according to the appendix ((Supplement)). Taking into account the compressor’s supporting position and supporting structure, the length and reinforcement of the casing, the shape of the casing and its After considering thickness and other factors, whenever possible, the allowable external force and external moment limits calculated according to Appendix C can be relaxed by about 10%. The seller should provide the allowable external force and external moment in the form of a table. The shell and support should be designed with sufficient strength and rigidity to limit the coaxiality error of the coupling caused by the application of allowable external forces and external moments to within 50um. 4.5 Rotating parts ||tt| |4.5.1 The shaft should be made of solid steel parts that have been heat treated and suitable for machining. Shafts with a diameter greater than 200mm after finishing should be made of forged steel parts. Shafts with a diameter equal to or less than 200mm after finishing can also be used. Made of forged steel parts, but with the buyer's consent, hot-rolled bars can also be used. The quality and heat treatment of the bars should comply with the standards for shaft forgings. 4.5.2 The shaft end mated with the coupling should comply with the provisions of ZBK54030 4.5. 3. If the buyer does not require other shaft protection measures, replaceable bushings should be installed at the interstage seal gap, all carbon ring seals and shaft air seals. Under specified use conditions, these bushings should be durable. Corrosive materials. Bushings with minimal clearance end seals should be suitably wear-resistant to prevent leakage between the ring and the bushing (see provisions in 4.10.1.7 Shaft-Sleeve). - The assembly design of the impeller should ensure that the rotor does not suffer temporary or permanent deformation under all specified operating conditions, including overspeed to trip speed, and the impeller assembly method should ensure sufficient coaxiality and maintain balance 4.5.5. The sensing surface of the radial vibration probe for detecting the rotor shaft should be coaxial with the bearing journal. All sensing surfaces of the rotating shaft (the two sensing surfaces for measuring radial vibration and axial displacement) should have no scratches or marks. Or any other surface discontinuity defects (such as oil holes and keyways). The surface should not be sprayed, coated and sleeved. Its final surface roughness R value should be 0.4-0.8um, and these sensing surfaces should be treated. Good demagnetization or other treatment so that the total electrical and mechanical runout value does not exceed the specified values ??in items and b: for the sensing surface of the radial vibration measurement probe, take the maximum allowable peak-to-peak amplitude of 25% or 6m The larger value; b. The sensing surface used for the axial displacement measurement probe is 13um. Note: If the above specified value cannot be achieved after using various methods, the buyer and seller should negotiate and propose other acceptance tests. Standard. 4.5.6 Each rotor should have a unique identifiable number. 4.5. A closed impeller composed of a disc, a blade and a wheel cover can be used. Semi-open impeller composed of disc and blades. The impeller can be of welded, riveted, milled or cast structure. If the buyer agrees, other manufacturing methods such as electroerosion and needle welding are also allowed. 4.5.8 Welding and riveting. Impellers can be made of forgings or castings. The welds in the flow channel should be smooth and free of welding spatter. The impeller should be heat treated after welding to eliminate internal stress. There should be no sharp edges at the inlet and outlet of the blade. 4.5.9 Cast impellers should be fully finished except for the flow passage. Repair welding is only allowed with the buyer's consent. 423
JB/T6443--92
4.5.10 Welding is not allowed to balance the impeller. 4.5.11 The design of parts subject to stress should give due consideration to the stress concentration caused by the geometric shape. The design of rotating parts subject to stress should adopt structures such as rounded corners that can reduce stress concentration (parts that should be noted include: the intersection of the impeller, blades and disc, keyway and shaft diameter reduction).
4.5.12 The overall thrust plate should be used first. When a removable floating ring type, mechanical contact type or gas type shaft seal is used, a replaceable thrust plate should be used. When the thrust plate and the shaft are integrated, the thrust plate must have an additional thickness of at least 3.2mm so that it can be repaired and processed when the thrust plate is damaged. When using replaceable thrust discs (for assembly and maintenance purposes), the thrust discs should be securely fastened to the shaft to prevent fretting wear. 4.5.13 The surface roughness R of the two thrust surfaces of the thrust plate should be 0.4μm, and the axial runout on either side of the thrust plate should not exceed 12.7tum.
4.5.14 allows the compressor to be designed without a balance plate. 4.5.15 If necessary, a balance plate, balance tube and balance air hole should be set up to reduce the axial load on the thrust bearing, and one or several pressure gauge joints should be set up to indicate the pressure in the balance chamber instead of the balance tube. in pressure. 4.5.16 The diameter of the balance pipe should be designed such that when the gap of the labyrinth seal is twice the original design value, the balance pipe can still transport the gas leakage of the balance plate without increasing the rated load of the thrust bearing ( See clause 4.6.3.3). 4.5.17 In order to prevent static voltage from being generated on the shaft, the residual magnetism of the rotating element should not exceed 0.0005T (Tesla). 4.6 Bearings and bearing boxes
4.6.1 General
4.6.1.1 Bearings should use wave body dynamic pressure radial bearings and thrust bearings. If other types of bearings are used, formal consent from the buyer is required. 4.6.1.2 Radial bearings and thrust bearings should be equipped with bearing metal temperature sensors according to the standards agreed between the buyer and the seller. 4.6.2 Radial bearings
4.6.2.1 Bushing type or tilting pad radial bearings should be used, and a split structure should be used to facilitate assembly. The use of any structure shall require the consent of the buyer. Bearings shall have precision-bored steel bearing bodies, replaceable babbitted bushings, pads or housings. Bearings should be equipped with anti-rotation pins and their shaft positioning should be ensured. 4.6.2.2 The bearing design should suppress the instability of the hydrodynamic pressure and provide sufficient damping within the entire allowable clearance range of the bearing, so that the vibration of the rotor can be limited to the specified value when the equipment is no-load or loaded at the specified operating speed. within the maximum amplitude (see 4.8.5.5). 4.6.2.3 Bushings, pads or shells should be installed in horizontally split bearing boxes and can be replaced. When replacing these parts, it is not necessary to disassemble the upper half of the casing of the horizontally split machine or the end cover of the vertically divided machine. Unless otherwise agreed to by the purchaser, the bearings shall be designed so that bushings, pads and bearing bodies may be replaced without disassembly of the inner sleeve of the coupling.
4.6.2.4 Compressors equipped with bushed radial bearings shall be designed so that the bearing housing cannot be reworked when tilting pad bearings are installed on site. 4.6.3 Thrust bearing
4.6.3.1 The hydrodynamic thrust bearing shall be a multi-piece sector-shaped steel bushing type of cast Babbitt alloy and shall be designed to have equal thrust capacity in both directions. , the arrangement shall be suitable for continuous pressure lubrication of each side. Both sides of the thrust bearing are tilted pads, which have the function of automatically balancing the load. Even if there is a slight deviation in the thickness of the pads, the tilting pad bearing can ensure that each pad bears an equal share of the load.
4.6.3.2 Pads should be designed and manufactured to thickness tolerances with precise dimensions to enable interchange or replacement of individual pads 4.6.3.3 Thrust bearing dimensions should be designed to operate under the most adverse conditions work continuously under the conditions. The calculation of thrust should include but not be limited to the following factors:
a.
The maximum design internal clearance of the seal and twice the maximum design internal clearance; b.
The diameter of the pressurized rotor step change;
c.
Maximum pressure difference between stages;
d.
The specified limit deviation of inlet, interstage and exhaust pressure; e.
The external thrust transmitted by the coupling;
When the motor is directly driven, the maximum thrust from the motor thrust. f.
424
3. If the buyer does not require other shaft protection measures, replaceable sleeves should be installed at the interstage seal gap, all carbon ring seals and shaft air seals. Under specified conditions of use, these bushings should be made of corrosion-resistant materials. Sleeves with extremely small gap end seals should be treated with appropriate wear resistance to prevent leakage between the ring and the sleeve (see the provisions of Article 4.10.1.7). 4.5.4 The assembly design of the shaft-sleeve-impeller should ensure that the rotor will not undergo temporary or permanent deformation. The impeller shall be assembled in a manner that ensures adequate concentricity and maintains balance under all specified operating conditions, including overspeed to trip speed. 4.5.5 The sensing surface of the radial vibration probe for detecting the rotor shaft should be coaxial with the bearing journal. All sensing surfaces of the rotating shaft (the two sensing surfaces that measure radial vibration and axial displacement) should be free of scratches, marks, or any other surface discontinuities (such as oil holes and keyways). The surface should not be sprayed, coated or sleeved. Its final surface roughness R. The value should be 0.4-0.8um. ??These sensing surfaces should be well demagnetized or otherwise treated so that the total electrical and mechanical runout value does not exceed the specified values ??in items and b: Transmission of radial vibration measurement probes Sensing surface, take the larger of 25% of the maximum allowable peak-to-peak amplitude or 6m; b. The sensing surface of the axial displacement measurement probe is 13um. Note: If the above specified value cannot be achieved after using various methods, the buyer and seller should negotiate and propose other acceptance standards that can be adopted. 4.5.6 Each rotor should have a unique identifiable number. This number should be marked on the shaft end without coupling. 4.5. A closed impeller composed of a disc, blades and a wheel cover or a semi-open impeller composed of a disc and blades can be used. The impeller can be of welded, riveted, milled or cast structure. If the buyer agrees, other manufacturing methods such as electroerosion and needle welding are also allowed. 4.5.8 Both welded and riveted impellers can be made of forgings or castings. The welds in the flow channel should be smooth and free of welding spatter. The impeller should be heat treated after welding to eliminate internal stress. There should be no sharp edges at the inlet and outlet of the blade. 4.5.9 Cast impellers should be fully finished except for the flow passage. Repair welding is only allowed with the buyer's consent. 423
JB/T6443--92
4.5.10 Welding is not allowed to balance the impeller. 4.5.11 The design of parts subject to stress should give due consideration to the stress concentration caused by the geometric shape. The design of rotating parts subject to stress should adopt structures such as rounded corners that can reduce stress concentration (parts that should be noted are: the intersection of the impeller, blades and disc, keyway and shaft diameter reduction).
4.5.12 The overall thrust plate should be preferred. When a removable floating ring type, mechanical contact type or gas type shaft seal is used, a replaceable thrust plate should be used. When the thrust plate and the shaft are integrated, the thrust plate must have an additional thickness of at least 3.2mm so that it can be repaired and processed when the thrust plate is damaged. When using replaceable thrust discs (for assembly and maintenance purposes), the thrust discs should be securely fastened to the shaft to prevent fretting wear. 4.5.13 The surface roughness R of the two thrust surfaces of the thrust plate should be 0.4μm, and the axial runout on either side of the thrust plate should not exceed 12.7tum.
4.5.14 allows the compressor to be designed without a balance plate. 4.5.15 If necessary, a balance plate, balance tube and balance air hole should be set up to reduce the axial load on the thrust bearing, and one or several pressure gauge joints should be set up to indicate the pressure in the balance chamber instead of the balance tube. in pressure. 4.5.16 The diameter of the balance pipe should be designed such that when the gap of the labyrinth seal is twice the original design value, the balance pipe can still transport the gas leakage of the balance plate without increasing the rated load of the thrust bearing ( See clause 4.6.3.3). 4.5.17 In order to prevent static voltage from being generated on the shaft, the residual magnetism of the rotating element should not exceed 0.0005T (Tesla). 4.6 Bearings and bearing boxes
4.6.1 General
4.6.1.1 Bearings should use wave body dynamic pressure radial bearings and thrust bearings. If other types of bearings are used, formal consent from the buyer is required. 4.6.1.2 Radial bearings and thrust bearings should be equipped with bearing metal temperature sensors according to the standards agreed between the buyer and the seller. 4.6.2 Radial bearings
4.6.2.1 Bushing type or tilting pad radial bearings should be used, and a split structure should be used to facilitate assembly. The use of any structure shall require the consent of the buyer. Bearings shall have precision-bored steel bearing bodies, replaceable babbitted bushings, pads or housings. Bearings should be equipped with anti-rotation pins and their shaft positioning should be ensured. 4.6.2.2 The bearing design should suppress the instability of the hydrodynamic pressure and provide sufficient damping within the entire allowable clearance range of the bearing, so that the vibration of the rotor can be limited to the specified value when the equipment is no-load or loaded at the specified operating speed. within the maximum amplitude (see 4.8.5.5). 4.6.2.3 Bushings, pads or shells should be installed in horizontally split bearing boxes and can be replaced. When replacing these parts, it is not necessary to disassemble the upper half of the casing of the horizontally split machine or the end cover of the vertically divided machine. Unless otherwise agreed to by the purchaser, the bearings shall be designed so that bushings, pads and bearing bodies may be replaced without disassembly of the inner sleeve of the coupling.
4.6.2.4 Compressors equipped with bushed radial bearings shall be designed so that the bearing housing cannot be reworked when tilting pad bearings are installed on site. 4.6.3 Thrust bearing
4.6.3.1 The hydrodynamic thrust bearing shall be a multi-piece sector-shaped steel bushing type of cast Babbitt alloy and shall be designed to have equal thrust capacity in both directions. , the arrangement shall be suitable for continuous pressure lubrication of each side. Both sides of the thrust bearing are tilted pads, which have the function of automatically balancing the load. Even if there is a slight deviation in the thickness of the pads, the tilting pad bearing can ensure that each pad bears an equal share of the load.
4.6.3.2 Pads should be designed and manufactured to thickness tolerances with precise dimensions to enable interchange or replacement of individual pads 4.6.3.3 Thrust bearing dimensions should be designed to operate under the most adverse conditions work continuously under the conditions. The calculation of thrust should include but not be limited to the following factors:
a.
The maximum design internal clearance of the seal and twice the maximum design internal clearance; b.
The diameter of the pressurized rotor step change;
c.
Maximum pressure difference between stages;
d.
The specified limit deviation of inlet, interstage and exhaust pressure; e.
The external thrust transmitted by the coupling;
When the motor is directly driven, the maximum thrust from the motor thrust. f.
424
3. If the buyer does not require other shaft protection measures, replaceable sleeves should be provided at the interstage seal gap, all carbon ring seals and shaft air seals. Under specified conditions of use, these bushings should be made of corrosion-resistant materials. Sleeves with extremely small gap end seals should be treated with appropriate wear resistance to prevent leakage between the ring and the sleeve (see the provisions of Article 4.10.1.7). 4.5.4 The assembly design of the shaft-sleeve-impeller should ensure that the rotor will not undergo temporary or permanent deformation. The impeller shall be assembled in a manner that ensures adequate concentricity and maintains balance under all specified operating conditions, including overspeed to trip speed. 4.5.5 The sensing surface of the radial vibration probe for detecting the rotor shaft should be coaxial with the bearing journal. All sensing surfaces of the rotating shaft (the two sensing surfaces that measure radial vibration and axial displacement) should be free of scratches, marks, or any other surface discontinuities (such as oil holes and keyways). The surface should not be sprayed, coated or sleeved. Its final surface roughness R. The value should be 0.4-0.8um. ??These sensing surfaces should be well demagnetized or otherwise treated so that the total electrical and mechanical runout value does not exceed the specified values ??in items and b: Transmission of radial vibration measurement probes Sensing surface, take the larger value of 25% of the maximum allowable peak-to-peak amplitude or 6m; b. The sensing surface of the axial displacement measurement probe is 13um. Note: If the above specified value cannot be achieved after using various methods, the buyer and seller should negotiate and propose other acceptance standards that can be adopted. 4.5.6 Each rotor should have a unique identifiable number. This number should be marked on the shaft end without coupling. 4.5. A closed impeller composed of a disc, blades and a wheel cover or a semi-open impeller composed of a disc and blades can be used. The impeller can be of welded, riveted, milled or cast structure. If the buyer agrees, other manufacturing methods such as electroerosion and needle welding are also allowed. 4.5.8 Both welded and riveted impellers can be made of forgings or castings. The welds in the flow channel should be smooth and free of welding spatter. The impeller should be heat treated after welding to eliminate internal stress. There should be no sharp edges at the inlet and outlet of the blade. 4.5.9 Cast impellers should be fully finished except for the flow passage. Repair welding is only allowed with the buyer's consent. 423
JB/T6443--92
4.5.10 Welding is not allowed to balance the impeller. 4.5.11 The design of parts subject to stress should give due consideration to the stress concentration caused by the geometric shape. The design of rotating parts subject to stress should adopt structures such as rounded corners that can reduce stress concentration (parts that should be noted include: the intersection of the impeller, blades and disc, keyway and shaft diameter reduction).
4.5.12 The overall thrust plate should be used first. When a removable floating ring type, mechanical contact type or gas type shaft seal is used, a replaceable thrust plate should be used. When the thrust plate and the shaft are integrated, the thrust plate must have an additional thickness of at least 3.2mm so that it can be repaired and processed when the thrust plate is damaged. When using replaceable thrust discs (for assembly and maintenance purposes), the thrust discs should be securely fastened to the shaft to prevent fretting wear. 4.5.13 The surface roughness R of the two thrust surfaces of the thrust plate should be 0.4μm, and the axial runout on either side of the thrust plate should not exceed 12.7tum.
4.5.14 allows the compressor to be designed without a balance plate. 4.5.15 If necessary, a balance plate, balance tube and balance air hole should be set up to reduce the axial load on the thrust bearing, and one or several pressure gauge joints should be set up to indicate the pressure in the balance chamber instead of the balance tube. in pressure. 4.5.16 The diameter of the balance pipe should be designed such that when the gap of the labyrinth seal is twice the original design value, the balance pipe can still transport the gas leakage of the balance plate without increasing the rated load of the thrust bearing ( See clause 4.6.3.3). 4.5.17 In order to prevent static voltage from being generated on the shaft, the residual magnetism of the rotating element should not exceed 0.0005T (Tesla). 4.6 Bearings and bearing boxes
4.6.1 General
4.6.1.1 Bearings should use wave body dynamic pressure radial bearings and thrust bearings. If other types of bearings are used, formal consent from the buyer is required. 4.6.1.2 Radial bearings and thrust bearings should be equipped with bearing metal temperature sensors according to the standards agreed between the buyer and the seller. 4.6.2 Radial bearings
4.6.2.1 Bushing type or tilting pad radial bearings should be used, and a split structure should be used to facilitate assembly. The use of any structure shall require the consent of the buyer. Bearings shall have precision-bored steel bearing bodies, replaceable babbitted bushings, pads or housings. Bearings should be equipped with anti-rotation pins and their shaft positioning should be ensured. 4.6.2.2 The bearing design should suppress the instability of the hydrodynamic pressure and provide sufficient damping within the entire allowable clearance range of the bearing, so that the vibration of the rotor can be limited to the specified value when the equipment is no-load or loaded at the specified operating speed. within the maximum amplitude (see 4.8.5.5). 4.6.2.3 Bushings, pads or shells should be installed in horizontally split bearing boxes and can be replaced. When replacing these parts, there is no need to disassemble the upper half of the casing of the horizontally divided machine or the end cover of the vertically divided machine. Unless agreed to by the purchaser, the bearings shall be designed so that bushings, pads and bearing bodies may be replaced without disassembly of the inner sleeve of the coupling.
4.6.2.4 Compressors equipped with bushed radial bearings shall be designed so that the bearing housing cannot be reworked when tilting pad bearings are installed on site. 4.6.3 Thrust bearing
4.6.3.1 The hydrodynamic thrust bearing shall be a multi-piece sector-shaped steel bushing type of cast Babbitt alloy and shall be designed to have equal thrust capacity in both directions. , the arrangement shall be suitable for continuous pressure lubrication of each side. Both sides of the thrust bearing are tilted pads, which have the function of automatically balancing the load. Even if there is a slight deviation in the thickness of the pads, the tilting pad bearing can ensure that each pad bears an equal share of the load.
4.6.3.2 Pads should be designed and manufactured to thickness tolerances with precise dimensions to enable interchange or replacement of individual pads 4.6.3.3 Thrust bearing dimensions should be designed to operate under the most adverse conditions work continuously under the conditions. The calculation of thrust should include but not be limited to the following factors:
a.
The maximum design internal clearance of the seal and twice the maximum design internal clearance; b.
The diameter of the pressurized rotor step change;
c.
Maximum pressure difference between stages;
d.
The specified limit deviation of inlet, interstage and exhaust pressure; e.
The external thrust transmitted by the coupling;
When the motor is directly driven, the maximum thrust from the motor thrust. f.
424
12 Integral thrust discs should be used first. When a removable floating ring type, mechanical contact type or gas type shaft seal is used, a replaceable thrust disc should be used. When the thrust disc is integral with the shaft, the thrust disc shall have an additional thickness of at least 3.2 mm so that the thrust disc can be repaired when damaged. When a replaceable thrust disc is used (for assembly and maintenance), the thrust disc shall be firmly fixed on the shaft to prevent micro-vibration wear. 4.5.13 The surface roughness R of the two thrust surfaces of the thrust disc shall be 0.4 μm, and the axial runout of the surface on either side of the thrust disc shall not exceed 12.7 tum.
4.5.14 The compressor can be designed as a structure without a balancing disc. 4.5.15 If necessary, a balancing disc, a balancing pipe and a balancing air hole shall be provided to reduce the axial load on the thrust bearing, and one or more pressure gauge joints shall be provided to indicate the pressure in the balancing chamber instead of the pressure in the balancing pipe. 4.5.16 The diameter of the balance pipe should be designed so that when the gap of the labyrinth seal is twice the original design value, the balance pipe can still transport the gas leakage of the balance disc without increasing the rated load value of the thrust bearing (see 4.6.3.3). 4.5.17 In order to prevent static voltage on the shaft, the residual magnetism of the rotating element should not exceed 0.0005T (Tesla). 4.6 Bearings and bearing boxes
4.6.1 General
4.6.1.1 Bearings should use wave-body dynamic pressure radial bearings and thrust bearings. If other types of bearings are used, the buyer's formal consent is required. 4.6.1.2 Radial bearings and thrust bearings should be installed with bearing metal temperature sensors according to the standards agreed upon by the buyer and the seller. 4.6.2 Radial bearings
4.6.2.1 Bushing-type or tilting pad radial bearings should be used, and a split structure should be used for ease of assembly. The use of a non-split structure should be approved by the buyer. Bearings shall have precision-bored steel bodies, replaceable babbitt-metal liners, pads, or housings. Bearings shall be provided with anti-rotation pins and shall ensure that they are located relative to the shaft. 4.6.2.2 Bearings shall be designed to suppress hydrodynamic instabilities and provide sufficient damping over the entire range of permissible bearing clearances to limit rotor vibration to the specified maximum amplitude when the machine is unloaded or loaded at the specified operating speed (see 4.8.5.5). 4.6.2.3 Bushings, pads, or housings shall be installed in horizontally split bearing housings and shall be replaceable. These parts shall be replaced without removing the upper housing of horizontally split machines or the end covers of vertically split machines. Unless otherwise agreed by the purchaser, bearings shall be designed so that the inner sleeve of the coupling can be replaced without removal of the inner sleeve of the coupling.
4.6.2.4 Compressors with sleeve-type radial bearings shall be designed so that tilting pad bearings can be installed in the field without remachining the bearing housing. 4.6.3 Thrust bearings
4.6.3.1 The hydrodynamic thrust bearings shall be of the multi-sector steel bushing type cast in babbitt alloy and shall be designed to have equal thrust capacity in both directions and shall be arranged to provide continuous pressure lubrication on each side. The thrust bearings shall be tilting pad type on both sides and shall have the function of automatically balancing the load. Even if there are slight deviations in the thickness of the pads, the tilting pad bearings can ensure that each pad bears an equal share of the load.
4.6.3.2 The pads shall be designed and manufactured with a thickness tolerance of precise dimensions to allow for interchangeability or replacement of individual pads. 4.6.3.3 The thrust bearings shall be designed to be able to operate continuously under the most unfavorable specified operating conditions. The thrust calculation shall include but not be limited to the following factors:
a.
The maximum design internal clearance of the seal and twice the maximum design internal clearance;
The step change of the diameter of the pressure rotor;
c.
The maximum pressure difference between stages;
d.
The limit deviation of the specified inlet, interstage and exhaust pressures;
The external thrust transmitted by the coupling;
The maximum thrust from the motor when the motor is directly driven. f.
424
12 Priority should be given to using the integral thrust plate. When a removable floating ring type, mechanical contact type or gas type shaft seal is used, a replaceable thrust plate should be used. When the thrust plate and the shaft are integrated, the thrust plate must have an additional thickness of at least 3.2mm so that it can be repaired and processed when the thrust plate is damaged. When using replaceable thrust discs (for assembly and maintenance purposes), the thrust discs should be securely fastened to the shaft to prevent fretting wear. 4.5.13 The surface roughness R of the two thrust surfaces of the thrust plate should be 0.4μm, and the axial runout on either side of the thrust plate should not exceed 12.7tum.
4.5.14 allows the compressor to be designed without a balance plate. 4.5.15 If necessary, a balance plate, balance tube and balance air hole should be set up to reduce the axial load on the thrust bearing, and one or several pressure gauge joints should be set up to indicate the pressure in the balance chamber instead of the balance tube. in pressure. 4.5.16 The diameter of the balance pipe should be designed such that when the gap of the labyrinth seal is twice the original design value, the balance pipe can still transport the gas leakage of the balance plate without increasing the rated load of the thrust bearing ( See clause 4.6.3.3). 4.5.17 In order to prevent static voltage from being generated on the shaft, the residual magnetism of the rotating element should not exceed 0.0005T (Tesla). 4.6 Bearings and bearing boxes
4.6.1 General
4.6.1.1 Bearings should use wave body dynamic pressure radial bearings and thrust bearings. If other types of bearings are used, formal consent from the buyer is required. 4.6.1.2 Radial bearings and thrust bearings should be equipped with bearing metal temperature sensors according to the standards agreed between the buyer and the seller. 4.6.2 Radial bearings
4.6.2.1 Bushing type or tilting pad radial bearings should be used, and a split structure should be used to facilitate assembly. The use of any structure shall require the consent of the buyer. Bearings shall have precision-bored steel bearing bodies, replaceable babbitted bushings, pads or housings. Bearings should be equipped with anti-rotation pins and their shaft positioning should be ensured. 4.6.2.2 The bearing design should suppress the instability of the hydrodynamic pressure and provide sufficient damping within the entire allowable clearance range of the bearing, so that the vibration of the rotor can be limited to the specified value when the equipment is no-load or loaded at the specified operating speed. within the maximum amplitude (see 4.8.5.5). 4.6.2.3 Bushings, pads or shells should be installed in horizontally split bearing boxes and can be replaced. When replacing these parts, there is no need to disassemble the upper half of the casing of the horizontally divided machine or the end cover of the vertically divided machine. Unless otherwise agreed to by the purchaser, the bearings shall be designed so that bushings, pads and bearing bodies may be replaced without disassembly of the inner sleeve of the coupling.
4.6.2.4 Compressors equipped with bushed radial bearings shall be designed so that the bearing housing cannot be reworked when tilting pad bearings are installed on site. 4.6.3 Thrust bearing
4.6.3.1 The hydrodynamic thrust bearing shall be a multi-piece sector-shaped steel bushing type of cast Babbitt alloy and shall be designed to have equal thrust capacity in both directions. , the arrangement shall be suitable for continuous pressure lubrication of each side. Both sides of the thrust bearing are tilted pads, which have the function of automatically balancing the load. Even if there is a slight deviation in the thickness of the pads, the tilting pad bearing can ensure that each pad bears an equal share of the load.
4.6.3.2 Pads should be designed and manufactured to thickness tolerances with precise dimensions to enable interchange or replacement of individual pads 4.6.3.3 Thrust bearing dimensions should be designed to operate under the most adverse conditions work continuously under the conditions. The calculation of thrust should include but not be limited to the following factors:
a.
The maximum design internal clearance of the seal and twice the maximum design internal clearance; b.
The diameter of the pressurized rotor step change;
c.
Maximum pressure difference between stages;
d.
The specified limit deviation of inlet, interstage and exhaust pressure; e.
The external thrust transmitted by the coupling;
When the motor is directly driven, the maximum thrust from the motor thrust. f.
424
Tip: This standard content only shows part of the intercepted content of the complete standard. If you need the complete standard, please go to the top to download the complete standard document for free.