API Std 617: 2002 Axial and Centrifugal Compressors and Expander-compressors for Petroleum, Chemical and Gas Industry Services

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3-33

ANNEX 3D

INSPECTOR’S CHECK LIST

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3-34 API STANDARD 617—CHAPTER 3

Item

Standard 617

Reviewed Observed Witnessed

Inspected

By StatusPar Ch

GENERAL

Contract Review—Testing and

Inspections Listed in Proposal

2.2.1.4 1

General Test Requirements 4.1.1

4.1.3

4.1.4

4.1.4.1

4.1.6

4.1.7

4.2.1

4.2.1.2

Cleanliness 4.2.1.3

4.2.1.4

Hardness 4.2.1.5 1

Nameplate 2.11.1

2.11.2

2.11.2.1

Rotation Arrows 2.11.3 3

MATERIAL INSPECTIONS

Material Inspections 4.2.2.1 1

Castings 2.2.2.1 1

Low Temperature Impact 2.2.1.15.5 1

Forgings 2.2.3.2 1

Weldings 2.2.4.1 1

Pressure-containing Casings 2.3.1 1

Material Inspection of Pressure-

containing Parts

2.3.1.12 1

ROTATING ELEMENT

Impellers 2.5.10.4

2.5.10.5

2.5.10.6

4.3.3.1

Overspeed 2.5.10.7

4.3.3.1

Balance 2.6.8

2.6.8.8

Annex B

Run-out 2.6.8.9

2.6.8.10

ACCESSORIES

Shaft End Seals 4.3.5

Annex D

Lubrication and Sealing Systems 2.10.3

API Std 614

Drivers 3.1 1

Steam Turbine 3.1.4

API Std 612

Motor 3.1.5

API Std 541

Gas Turbine 3.1.7

API Std 616

Separate Gear Units 3.1.8

API Std 613

Coupling and Guard 3.2

API Std 671

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AXIAL AND CENTRIFUGAL COMPRESSORS AND EXPANDER-COMPRESSORS FOR PETROLEUM, CHEMICAL AND GAS INDUSTRY SERVICES 3-35

Instrumentation 3.4.3

3.4.4

API Std 614

API Std 670

Alarms and Shutdowns 3.4.5

API Std 614

Electrical Systems 3.4.6

API Std 614

2.1.14

Piping 3.5.1

API Std 614

Special Tools 3.6.1

3.6.2

HYDROSTATIC TEST

Hydrostatic Test 4.3.2.1

4.3.2.2

4.3.2.3

OVERSPEED TEST

Impeller Overspeed Test 4.3.3.1 1

MECHANICAL RUNNING TEST

Unbalance Response Veriﬁcation 2.6.3.1 1

Vibration Record 2.6.3.1.1

4.3.6.1.1

4.3.6.1.2

4.3.6.1.3

Contract Shaft Seals Used in Test 4.3.6.1.4

4.3.1.1.1

Oil Flow Rates P. & T. 4.3.1.1.3 3

Oil System Clean 4.3.1.1.4 3

Warning Protective Control

Devices Checked

4.3.1.1.6 3

Connections Check for Leaks 4.3.1.1.5 3

Test Coupling Used 4.3.1.1.8 3

Vibration Levels 4.3.1.1.11 3

Test Speeds Performed 4.3.1.2.1 3

Test Run at Trip Speed 4.3.1.2.2 3

4-hour Test Run 4.3.1.2.3 3

Seal Flow Data 4.3.1.2.4 3

Lube and Seal Oil Flows Varied 4.3.6.1.5 1

Vibration Levels 4.3.1.3.1

4.3.1.3.2

4.3.1.3.3

Lateral Critical Speed Veriﬁed 4.3.1.3.3 2

Unbalance Response Analysis

Veriﬁed

4.3.1.3.5

4.3.1.3.6

Spare Rotor Tested 4.3.1.4.2 3

Assembled Compressor Gas Leak 4.3.2

4.3.2.1

4.3.2.2

4.3.2.3

OPTIONAL TESTING

Performance Test 4.3.3.1

4.3.3.1.1

4.3.3.1.2

4.3.3.1.3

4.3.3.1.4

4.3.3.1.5

Item

Standard 617

Reviewed Observed Witnessed

Inspected

By StatusPar Ch

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3-36 API STANDARD 617—CHAPTER 3

Complete Test Unit 4.3.3.2 3

Gear Test—Stand Alone 4.3.3.3 3

Full-speed Test 4.3.1.2.3 3

Helium Test 4.3.8.2 1

Sound-level Test 4.3.8.3 1

Auxiliary Equipment Test 4.3.8.4 1

Post-test Inspection of

Compressor Internal

4.3.8.5 1

Full-pressure/Full-load/

Full-speed Test

4.3.8.6 1

Post-test Inspection of Hydraulic

Coupling Fit

4.3.8.7 1

Spare Parts Test 4.3.8.8 1

PREPARATION FOR SHIPMENT

Equipment Prepared 4.4.1

4.4.2

Paint 4.4.3.1 1

Exterior Machined

Surfaces Coated

4.4.3.2 1

Bearing Housings, Oil Systems,

Auxiliary Equipment and Piping

Preserved

4.4.3.4 1

Openings Covered and Protected 4.4.3.5

4.4.3.6

4.4.3.7

Lifting Points Identiﬁed 4.4.3.8 1

Equipment Identiﬁed, Tagged,

Packing List

4.4.3.9 1

Spare Rotor Prepared for Storage 4.4.3.10 1

Exposed Shafts, etc. Prepared for

Shipment

4.4.3.12 1

Auxiliary Piping Connections

Tagged or Stamped

4.4.4

4.4.5

Installation, Instructions Shipped

with Equipment

4.4.6 1

Gear Contact Checks 4.2.1

4.2.1.1

4.2.1.2

Tooth Mesh Inspection 4.3.1.4.1 3

Item

Standard 617

Reviewed Observed Witnessed

Inspected

By StatusPar Ch

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3-37

ANNEX 3E

EXTERNAL FORCES AND MOMENTS

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3-38 API STANDARD 617—CHAPTER 3

For integrally geared compressors, it is not possible to give

a formula to calculate the maximum allowable piping forces

and moments on each casing ﬂange. The limiting criteria are

the gear contact pattern and the impeller/stator gap. The max-

imum value of the external forces and moments, which leads

to acceptable deformations and therefore acceptable changes

of the gear contact pattern and the impeller/stator gap,

depends on various parameters.

These parameters include:

Volute geometry, volute wall thickness, length of overhang,

gear case geometry and gear case wall thickness. The possi-

ble combinations are nearly endless.

Each manufacturer has limits based on his own experience

for each volute size and gear case combination for a given

speciﬁc machine. The values are available from the manufac-

turer with the quotation.

It is a common practice on integrally geared compressors

to supply expansion joints in order to minimize the piping

loads on the machine ﬂanges and to insure that piping loads

are within the allowable limits for the particular unit.

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3-39

ANNEX 3F

RATING FORMULAS FOR INTEGRALLY

GEARED COMPRESSOR GEARING

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3-40 API STANDARD 617—CHAPTER 3

The rating formula’s given below are based on the methods

from AGMA 2101. The constant of 0.8 at the beginning of the

formulas below is to provide increased reliability.

F.1 Pitting Resistance Power Rating

The pitting resistance allowable transmitted power, P

, for

a gear set is:

(3.F-1)

where

= pinion speed (rpm),

b = face width (mm),

w1=

operating pitch diameter of pinion (mm) =

2a/(u – 1),

a = center distance (mm),

u = gear tooth ratio (never less than 1.0),

= elastic coefﬁcient = 190 for steel pinion and

gear,

= geometry factor (reference AGMA 908).

F.2 Bending Strength Power Rating

The bending strength allowable transmitted power, P

, for

a gear pair is:

(3.F-2)

where

= transverse module (equal to normal module

divided by the cosine of the helix angle at the

standard pitch diameter),

= geometry Factor (reference AGMA 908).

F.3 Load Distribution Factor,

If the value of K

calculated below is less than 1.1, then

1.1 shall be used as the value of K

. Gear designs shall not

result in a calculated value of K

over 1.50 without approval

from the purchaser.

= 1.0 + 0.8 (K

Hpf

+ 0.054 + 0.4032 ×

-3

b – 1.152 × 10

-7

) (3.F-3)

where

b = face width of narrower member of gear set

(mm)

Hpf

= bod – 0.025

when b ≤ 25 mm

= bod – 0.0375 + 0.000492 b

when 25 < b < 432

= bod – 0.1109 + 0.000815 b – 3.53 × 10

-7

when 432 < b ≤ 1020

bod = the greater of 0.05 or b/(10 d

)

Note: The distance from the center of the gear mesh to the center of

the bearing span divided by the bearing span must be less than 0.175.

The tooth contact must be checked at assembly, with contact adjust-

ments as required. If these conditions are not met, or for wide face

gears, an analytical approach may be used to determine a more con-

servative load distribution factor, with prior approval by the purchaser.

F.4 Dynamic Factor,

ISO 1328 Grade 5 = > K

= 1.135

ISO 1328 Grade 4 = > K

= 1.120

ISO 1328 Grade 3 = > K

= 1.105

ISO 1328 Grade 2 = > K

= 1.090

The dynamic factor, K

, does not account for dynamic

tooth loads that may occur due to torsional or lateral natural

frequencies. System designs should avoid having such natural

frequencies close to an excitation frequency associated with

an operating speed since the resulting gear tooth dynamic

loads may be very high.

F.5 Stress Cycle Factors,

and

= 2.466 N

-0.056

, pitting stress cycle (life) factor,

= 1.6831 N

-0.0323

, bending stress cycle (life) factor.

N is the number of stress cycles,

N = pinion RPM 1.052 × 10

for the pinion,

N = bull gear RPM × 1.052 × 10

× number of pin-

ions in mesh for the bull gear.

Note: These factors are based on the lower line in Figures 17 and 18

of ANSI/AGMA 2101-C95 with 175,316 hours (20 years

× 365.242

days/year

× 24 hours/day) of continuous service at rated operating

speed.

F.6 Allowable Stress Numbers, σσ

σσ

and

σσ

The values of σ

and σ

shall be for Grade 2 materials

per ANSI/AGMA 2101-C95, Clause 16.

0.8

1.91

×10

---------------------





----------------------





-----------------------





0.8

1.91

×10

---------------------





------------------------------





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AXIAL AND CENTRIFUGAL COMPRESSORS AND EXPANDER-COMPRESSORS FOR PETROLEUM, CHEMICAL AND GAS INDUSTRY SERVICES 3-41

F.7 Reverse Loading

For idler gears and other gears where the teeth are com-

pletely reverse loaded on every cycle, use 70% of the allow-

able bending stress number, σ

, in ANSI/AGMA 2101-C95.

F.8 Service Factor,

and

The service factor used for integrally geared centrifugal

compressors shall be 1.4 when driven by an induction motor,

1.6 when driven by a gas or steam turbine, and 1.7 when

driven by a synchronous motor or internal combustion engine.

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