HSC Notice 8

8/10/2019 HSC Notice 8

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ABS GUIDE FOR BUILDING AND CLASSING HIGH SPEED CRAFT . 2001 1

GUIDE FOR BUILDING AND CLASSING

HIGH SPEED CRAFTOCTOBER 2001

NOTICE NO. 8 November 2009

The following Rule Changes were approved by the ABS Rules Committee on 3 June 2008and 18 June 2009 and become EFFECTIVE AS OF 1 JANUARY 2010.

Notes - The date in the parentheses means the date that the Rule becomes effective for new constructionbased on the contract date for construction, unless otherwise noted. (See 1-1-4/3.3 of the ABS

Rules for Conditions of Classification (Part 1).)

PART 3 HULL CONSTRUCTION AND EQUIPMENT

SECTION 4 KEELS, STEMS, STERN FRAMES, SHAFT STRUTS, AND PROPELLERNOZZLES

(Revise Section title as above and add new Subsection 3/4.19, as follows.)

3/4.19 Propeller Nozzles (2010)

3/4.19.1 Application

The requirements in this section are applicable for propeller nozzles with inner diameterd of 5 meters(16.4 feet) or less. Nozzles of larger inner diameter are subject to special consideration with allsupporting documents and calculations submitted for review.

3/4.19.2 Design Pressure

The design pressure of the nozzle is to be obtained from the following:

=

pd A

N c p 610 N/mm2 (kgf/mm2, psi)

where

c = coefficient as indicated in Table 3/4.1

= coefficient as indicated in Table 3/4.2, but not to be taken less than 10

N = maximum shaft power, in kW (hp)

A p = propeller disc area

=4

2 D , in m2 (ft2)

D = propeller diameter, in m (ft)


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Notice No. 8 November 2009

2 ABS GUIDE FOR BUILDING AND CLASSING HIGH SPEED CRAFT . 2001

TABLE 3/4.1 Coefficient c (2009)

c Propeller Zone(see 3-2-7/Figure 1) pd in N/mm

2 pd in kgf/mm2 pd in psi

2 10.0 1.02 11.62 103 1 & 3 5.0 0.51 5.81 103

4 3.5 0.36 4.067 103

TABLE 3/4.2 Coefficient (2009)

pd in N/mm2 pd in kgf/mm

2 pd in psi

p A

N 210221

p A

N 210221

p A

N 2101621

3/4.19.3 Nozzle Cylinder

a Shell Plate Thickness. The thickness of the nozzle shell plating, in mm (in.), is not to be lessthan:

t = t o + t c, but not to be taken less than 7.5 (0.3) mm (in.)

where

t o = thickness obtained from the following formula:

= d pn pS c mm (in.)

cn = coefficient as indicated in Table 3/4.3

S p = spacing of ring webs in mm (in.)

pd = nozzle design pressure in N/mm2 (kgf/mm2, psi), as defined in 3/4.19.2

t c = corrosion allowance determined by Table 3/4.4

K n = nozzle material factor as defined in 3/5.1.2

TABLE 3/4.3 Coefficient cn (2009)

pd in N/mm2 pd in kgf/mm

2 pd in psi

cn 1.58 10-1 4.95 10-1 1.32 10-2


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TABLE 3/4.4 Coefficient t c (2009)

Value of t o t c mm (in.)

If t o 10.0 (0.4) 1.5 (0.06)

If t o > 10.0 (0.4) the lesser ofb1, b2 whereb1 = 3.0 (0.12) mm (in.)

12 105

+=

n

o

K

t b mm or 12 102.0

+=

n

o

K

t b in.

b Internal Diaphragm Thickness. Thickness of nozzle internal ring web is not to be less thanthe required nozzle shell plating for Zone 3.3/4.19.4 Nozzle Section Modulus

The minimum requirement for nozzle section modulus is obtained from the following formula:

SM = d 2 b V d 2 Q n cm3 (in3)

where

d = nozzle inner diameter, in m (ft)

b = nozzle length, in m (ft)

V d = design speed in ahead condition, in knots, as defined in 3/5.2.1

Q = reduction factor conditional on material type= 1.0 for ordinary strength steel

= 0.78 for H32 strength steel= 0.72 for H36 strength steel= 0.68 for H40 strength steel

Q factor for steel having yield strength other than above is to be speciallyconsidered.

n = nozzle type coefficient taken equal to 0.7 (0.0012) for fixed nozzles


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FIGURE 3/4.1 Nozzle Ring Section View (2009)

b d

Zone 1Zone 2Zone 3

Zone 4

3/4.19.5 Welding Requirement

The inner and outer nozzle shell plating is to be welded to the internal stiffening ring webs withdouble continuous welds as far as practicable. Plug/slot welding is prohibited for the inner shell, butmay be accepted for the outer shell plating, provided that the nozzle ring web spacing is not greaterthan 350 mm (13.8 in.).


SECTION 5 RUDDERS (2009)

(Revise Section 3/5, as follows.)

3/5.1 General

3/5.1.1 Application

Requirements specified in this Section are applicable to:

i) Ordinary profile rudders described in Table 3/5.1A with rudder operating angle range from 35 to +35.

ii) High-lift rudders described in Table 3/5.1B, the rudder operating angle of which might beexceeding 35 on each side at maximum design speed.

Rudders not covered in Table 3/5.1A nor in Table 3/5.1B are subject to special consideration, provided that all the required calculations are prepared and submitted for review in full compliancewith the requirements in this section.

Special consideration will be given to aluminum rudder stocks and fiber reinforced plastic rudders andrudder stocks. Material specifications are to be listed on the plans.


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3/5.1.2 Rudder and Rudder Stock Materials

Rudder stocks, pintles, coupling bolts, and keys are to be of material in accordance with the requirementsof Chapter 1 of the ABS Rules for Materials and Welding (Part 2) . The Surveyor needs not witnessmaterial tests for coupling bolts and keys. The surfaces of rudder stocks in way of exposed bearingsare to be of non-corrosive material.Material factors of castings and forgings used for the shoe piece ( K g ), horn ( K h), stock ( K s), bolts ( K b),coupling flange ( K f ), pintles ( K p), and nozzles ( K n) are to be obtained for their respective material fromthe following equation:

K = (n y /Y )e

wheren y = 235 N/mm2 (24 kgf/mm2, 34000 psi)

Y = specified minimum yield strength of the material, in N/mm2 (kgf/mm2, psi), but isnot to be taken as greater than 0.7U or 450 N/mm2 (46 kgf/mm2, 65000 psi),

whichever is lesserU = minimum tensile strength of material used, in N/mm2 (kgf/mm2, psi)

e = 1.0 forY 235 N/mm2 (24 kgf/mm2, 34000 psi)= 0.75 forY > 235 N/mm2 (24 kgf/mm2, 34000 psi)

3/5.1.3 Expected Torque

The torque considered necessary to operate the rudder in accordance with 4/8.8.2, is to be indicated onthe submitted rudder or steering gear plan. See 4/8.1.3 and 3/5.2.2c.

Note that this expected torque is not the design torque for rudder scantlings.

3/5.1.4 Rudder StopsStrong and effective structural rudder stops are to be fitted. Where adequate positive mechanical stopsare provided within the steering gear in accordance with 4/8.3.1, structural stops will not be required.

3/5.2 Rudder Design Force

Rudder force,C R, upon which rudder scantlings are to be based, is to be obtained from equation describedeither in Section 3/5.2.1 or Section 3/5.2.2 as applicable. Where for the ordinary rudders the rudderangle,, exceeds 35, the rudder force,C R, is to be increased by a factor of 1.74 sin ().3/5.2.1 Rudder Blades without Cutouts

Where the rudder profile can be defined by a single quadrilateral, the rudder force is to be obtained

from the following equation.C R = n k Rk ck l AV R2 kN (tf, Ltf)

where

n = 0.132 (0.0135, 0.00123)

k R = (b2/ At + 2)/3 but not taken more than 1.33

b = mean height of rudder area, in m (ft), as determined from Figure 3/5.1 At = sum of rudder blade area, A, and the area of rudder post or rudder horn within the

extension of rudder profile, in m2 (ft2)


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A = total projected area of rudder as illustrated in Figure 3/5.11, in m2 (ft2)For steering nozzles , A is not to be taken less than 1.35 times the projected area ofthe nozzle.

k c = coefficient depending on rudder cross section as indicated in Table 3/5.1A and

3/5.1B. For cross section differing from those in Table 3/5.1A and 3/5.1B,k c issubject to special consideration.

k l = coefficient as specified in Table 3/5.2

V R = craft speed, in knots

= for ahead conditionV R equalsV d or V min, whichever is greater

= for astern conditionV R equalsV a or 0.5V d , or 0.5V min, whichever is greater

V d = design speed in knots with the craft running ahead at the maximum continuousrated shaft rpm and at the summer load waterline

V a = maximum astern speed in knotsV min = (V d + 20)/3

3/5.2.2 Rudder Blades with Cutouts

This paragraph applies to rudders with cutouts (semi-spade rudders), such that the whole blade areacannot be adequately defined by a single quadrilateral. See Figure 3/5.2. Equations derived in this paragraph are based on a cutout blade with two quadrilaterals. Where more quadrilaterals are neededto define the rudder shape, similar rules apply.The total rudder force described in 3/5.2.1 is applicable for rudders with cutout(s), with A being thesummation of sub-quadrilaterals that make up the whole area of the rudder blade. Rudder force

distribution over each quadrilateral is to be obtained from the following equations:C R1 = C R A1/ A kN (tf, Ltf)

C R2 = C R A2/ A kN (tf, Ltf)

where

C R and A are as defined in 3/5.2.1

A1 and A2 are as described in Figure 3/5.2.


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TABLE 3/5.1A Coefficient k c for Ordinary Rudders (2009)

k c Profile Type Ahead Condition Astern Condition

1 Single plate 1.0 1.0

2 NACA-OOGttingen

1.1 0.80

3Flat side

1.1 0.90

4Mixed(e.g., HSVA) 1.21 0.90

5Hollow

1.35 0.90

TABLE 3/5.1B Coefficient k c for High-Lift/Performance Rudders (2009)

k c Profile Type Ahead Condition Astern Condition

1Fish tail

(e.g., Schilling high-liftrudder) 1.4 0.8

2Flap rudder

1.7 1.3

3

Rudder with steering nozzle

1.9 1.5


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FIGURE 3/5.1 Rudder Blade without Cutouts (2009)

x3 + x

2 - x

1 - x

42

z 3 + z 4 - z 2 - z 12b=

c=

4

3

21

A f

c

A

Rudder Stock Centerline

z (vert)

x (fwd)

b

A (see 3/5.2.1)

A f (see 3/5.3.2)

FIGURE 3/5.2 Rudder Blade with Cutouts (2009)

x6 + x3 - x4 - x72

z 3 + z 4 - z 2 - z 12b=

c1=

x2 + x5 - x1 - x72c2=

z (vert)

x (fwd)

4

3

21

7 5

6

A1 f

A2 f

Rudder Stock Centerline

C 1

b

A1

A1 f , A2 f (see 3/5.3.3)

C 2

A2

A2 (see 3/5.2.2)

A1 (see 3/5.2.2)


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3/5.3 Rudder Design Torque

3/5.3.1 General

The rudder design torque,Q R, for rudder scantling calculations is to be in accordance with 3/5.3.2 or

3/5.3.3 as applicable.3/5.3.2 Rudder Blades without Cutouts

Rudder torque,Q R, is to be determined from the following equation for both ahead and astern conditions.

Q R = C Rr kN-m (tf-m, Ltf-ft)

where

C R = rudder force as calculated in 3/5.2.1

r = c( k ) (but not less than 0.1c for ahead condition)c = mean breadth of rudder area, as shown in Figure 3/5.1, in m (ft)

= coefficient as indicated in Table 3/5.3k = A f / A

A f = area of rudder blade situated forward of the centerline of the rudder stock, in m2 (ft2),as shown in Figure 3/5.1

A = whole rudder area as described in 3/5.2.1

TABLE 3/5.2 Coefficient k l (2009)

Rudder/Propeller Layout k l Rudders outside propeller jet 0.8Rudders behind a fixed propeller nozzle 1.15

All others 1.0

TABLE 3/5.3 Coefficient (2009)

Rudder Positionor High-lift Ahead Condition Astern Condition

Located behind a fixedstructure, such as a rudderhorn

0.25 0.55

Located where no fixedstructure forward of it 0.33 0.66

High-Lift Rudders(see Table 3/5.1B)

Specialconsideration

(0.40 if unknown)

Specialconsideration


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3/5.3.3 Rudder Blades with Cutouts

This paragraph refers to rudder blades with cutouts (semi-spade rudders) as defined in 3/5.2.2.Equations derived in this paragraph are based on a cutout blade with two quadrilaterals. Where morequadrilaterals are needed to define the rudder shape, similar rules apply.Total rudder torque,Q R, in ahead and astern conditions is to be obtained from the following equation:

Q R = C R1 r 1 + C R2 r 2 kN-m (tf-m, Ltf-ft)

but not to be taken less thanQ Rmin in the ahead condition

whereQ Rmin = 0.1C R ( A1c1 + A2c2)/ A r 1 = c1( k 1 ) m (ft)r 2 = c2( k 2 ) m (ft)

c1, c

2 = mean breadth of partial area A

1, A

2, from Figure 3/A2

= coefficient as indicated in Table 3/A.3

k 1, k 2 = A1 f / A1, A2 f / A2 where A1 f , A2 f = area of rudder blade situated forward of thecenterline of the rudder stock for each part of the rudder, as shown in Figure3/A.2

C R, C R1, C R2, A1, A2 are as defined in 3/5.2.2.

3/5.3.4 Trial Conditions

The above equations forQ R are intended for the design of rudders and should not be directlycompared with the torque expected during the trial (see 3/5.1.3) or the rated torque of steering gear(see 4/8.1.3).

3/5.5 Rudder Stocks

3/5.5.1 Upper Rudder Stocks

The upper rudder stock is that part of the rudder stock above the neck bearing or above the top pintle,as the case may be.

3S Ru K Q N S = mm (in.)

where

N u = 42.0 (89.9, 2.39)

Q R = rudder torque, as defined in 3/5.3, in kN-m (tf-m, Ltf-m) K s = material factor for upper rudder stock, as defined in 3/5.1.2

3/5.5.2 Lower Rudder Stocks

In determining lower rudder stock scantlings, values of rudder force and torque calculated in 3/5.2 and3/5.3 are to be used. Bending moments, shear forces, as well as the reaction forces are to bedetermined from 3/5.5.3 and 3/5.11.3, and are to be submitted for review. For rudders supported byshoe pieces or rudder horns, these structures are to be included in the calculation model to account forsupport of the rudder body. Guidance for calculation of these values is given in Appendix 3/A.


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The lower rudder stock diameter is not to be less than obtained from the following equation:

6 2))(3/4(1 R M/QS S +=l mm (in.)where

S = upper stock required diameter from 3/5.5.1, in mm (in.)

S l = lower stock required diameter.

M = bending moment at the station of the rudder stock considered, in kN-m (tf-m, Ltf-ft)

Q R = rudder torque from 3/5.3, in kN-m (tf-m, Ltf-ft)

Above the neck bearing a gradual transition is to be provided where there is a change in the diameterof the rudder stock.

3/5.5.3 Bending Moments

The bending moment on the rudder and rudder stock may be determined in accordance with Appendix3/A or in accordance with the following equations:

a Spade Rudders

M n = C R l n kN-m (Ltf-ft)

M s = c R A A

C l1 kN-m (Ltf-ft)

where

M n = bending moment at neck bearing.

M s = bending moment at section under consideration.

ln = distance from center of neck bearing to the centroid of rudder area, m (ft)

lc = distance from section under consideration to the centroid of rudder area,

A1, m (ft)

A1 = area below section under consideration, m2 (ft2)

C R and A are defined in 3/5.2.

b Balanced Rudders with Shoepiece Support The bending moment at the neck bearing may be taken as indicated below. Bending momentsat other locations are to be determined by direct calculation and are to be submitted. See

Appendix 3/A for guidance in calculating bending moments. M n = NC Rl b kN-m (Ltf-ft)

where M n = bending moment at neck bearingl

b = distance between center of neck bearing and center of shoepiece pintle bearing, m (ft)

N =

++

+

u

b

b

u

I I

l

l

11

85.0

1

1


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1 =b

d

s

b

I I

3

3

l

l

I d = mean moment of inertia of shoepiece about the vertical axis, cm4 (in4)

l s = distance between center of shoepiece pintle bearing and the effective

support point of the shoepiece in the hull, m (ft)

I b = mean moment of inertia of the rudder, cm4 (in4), considering a width ofrudder plating twice the athwartship dimension of the rudder andexcluding welded or bolted cover plates for access to pintles, inc.

lu = distance between center of the neck bearing and the center of the rudder

carrier bearing, m (ft)

I u = mean moment of inertia of rudder stock, between neck bearing andrudder carrier bearing, cm4, (in4)

C R is as defined in 3/5.2.3/5.7 Flange Couplings

3/5.7.1 General

Rudder flange couplings are to comply with the following requirements:

i) Couplings are to be supported by an ample body of metal worked out from the rudder stock.

ii) The smallest distance from the edge of the bolt holes to the edge of the flange is not to be lessthan two-thirds of the bolt diameter.

iii) Coupling bolts are to be fitted bolts.

iv) Suitable means are to be provided for locking the nuts in place.In addition to the above, rudder flange couplings are to meet the type-specific requirements in 3/5.7.2(horizontal couplings) or 3/5.7.3 (vertical couplings) as applicable.

3/5.7.2 Horizontal Couplings

a Coupling Bolts There are to be at least six coupling bolts in horizontal couplings, and the diameter,d b, ofeach bolt is not to be less than obtained by the following equation:

d b = 0.62 )/(3

sb s nrK K d mm (in.)

whered s = required rudder stock diameter,S (3/5.5.1) orS l (3/5.5.2) as applicable, in

way of the coupling

n = total number of bolts in the horizontal coupling

r = mean distance, in mm (in.), of the bolt axes from the center of the boltsystem

K b = material factor for bolts, as defined in 3/5.1.2

K s = material factor for stock, as defined in 3/5.1.2


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b Coupling Flange Coupling flange thickness is not to be less than the greater of the following equations:

t f = d bt )/( b f K K mm (in.)

t f = 0.9d bt mm (in.)

where

d bt = calculated bolt diameter as per 3/5.7.2a based on a number of bolts notexceeding 8

K f = material factor for flange, as defined in 3/5.1.2

K b = material factor of bolts, as defined in 3/5.1.2

3/5.7.3 Vertical Couplings

a Coupling Bolts There are to be at least eight coupling bolts in vertical couplings and the diameter,d b, of each bolt is not to be less than obtained from the following equation:

d b = 0.81d s )/( sb nK K mm (in.)

where

n = total number of bolts

d s, K b, K s are as defined in 3/5.7.2.

In addition, the first moment of area,m, of the bolts about the center of the coupling is not to be less than given by the following equation:

m = 0.00043d s3 mm3 (in3)

where

d s = diameter as defined in 3/5.7.2

b Coupling Flange Coupling flange thickness,t f , is not to be less thand b, as defined in 3/5.7.3a.

3/5.9 Tapered Stock Couplings

3/5.9.1 Coupling Taper

Tapered stock couplings are to comply with the following general requirements in addition to type-specific requirements given in 3/5.9.2 or 3/5.9.3 as applicable:

i) Tapered stocks, as shown in Figure 3/5.3, are to be effectively secured to the rudder casting by a nut on the end.

ii) Taper length (l ) in the casting is generally not to be less than 1.5 times the stock diameter (d o)at the top of the rudder.

iii) The taper on diameter (c) is to be 1/12 to 1/8 for keyed taper couplings and 1/20 to 1/12 forcouplings with hydraulic mounting/dismounting arrangements, as shown in the followingtable.

iv) Where mounting with an oil injection and hydraulic nut, the push-up oil pressure and the push-up length are to be specially considered upon submission of calculations.


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Type of Coupling Assembly c =l

uo d d

Without hydraulicmounting/dismounting 1/12 c 1/8

With hydraulicmounting/dismounting 1/20 c 1/12

FIGURE 3/5.3 Tapered Couplings (2009)

d o

d u

d g

d n

hn

l d o

1

. 5

Locking Nut

a) Keyed Fitting

d o

d u

d g

d 1

SecuringFlat Bar

b) Keyless Fitting

l d o

1

. 5

3/5.9.2 Keyed Fitting

Where the stock is keyed,the key is to be fitted in accordance with the following:

i) The top of the keyway is to be located well below the top of the rudder.

ii) Torsional strength of the key equivalent to that of the required upper stock is to be provided.

iii) The effective shear area* of the key is not to be less than Ak , given below.

K

S

md k Y

Y

r S

A =1.5

3

where

Ak = shear area of key; mm2 (in2)

S = required upper stock diameter; mm (in.); as determined by 3/5.5.1

r md = offered radius of tapered stock at mid length of the bearing surface of thekey; mm (in.)

Y S = specified minimum yield strength of keyway material; N/mm2 (kgf/mm2,

psi)Y K = specified minimum yield strength of key material; N/mm2 (kgf/mm2, psi)


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iv) In general, the key material is to be at least of equal strength to the keyway material. For keysof higher strength materials, shear and bearing areas of keys and keyways may be based onthe respective material properties of the keys and the keyways, provided that compatibilitiesin mechanical properties of both components are fully considered. In no case, is the bearingstress of the key on the keyway to exceed 90% of the specified minimum yield strength of thekeyway material.

* Note: The effective area is to be the gross area reduced by any area removed by saw cuts, set screw holes, chamfer, etc.,and is to exclude the portion of the key in way of spooning of the key way.

3/5.9.3 Keyless Fitting

Hydraulic and shrink fit keyless couplings are to be fitted in accordance with the following:

i) Hydraulic pressure is to be specially considered upon submittal of detailed preloading stresscalculations and fitting instructions;

ii) The calculated torsional holding capacity is to be at least 2.0 times the transmitted torque based on the steering gear relief valve setting;

iii) Preload stress is not to exceed 70% of the minimum yield strength of either the stock or the bore;

iv) Prior to applying hydraulic pressure, at least 75% of theoretical contact area of rudder stockand rudder bore is to be achieved in an evenly distributed manner;

v) The upper edge of the upper main piece bore is to have a slight radius;

vi) The locking nut is to be fitted in accordance with 3/5.9.4.

3/5.9.4 Locking Nut

Dimensions of the securing nut, as shown in Figure 3/5.3, are to be proportioned in accordance withthe following and the nut is to be fitted with an effective locking device.

Height hn 0.6 d g Outer diameter of nut d n 1.2d u or 1.5d g , whichever is greaterExternal thread diameter d g 0.65 d o

In the case of a hydraulic pressure secured nut, a securing device such as a securing flat bar is to be provided. Calculations proving the effectiveness of the securing device are to be submitted.

3/5.11 Pintles

3/5.11.1 General

i) Pintles are to be fitted in the gudgeons by conical attachment to the full extent of the gudgeon

depthii) The depth of the pintle boss is not to be less than the required pintle diameterd p, and bearing

length is to between 1.0 and 1.2 timesd p.

iii) The taper on the diameter is to be:1/12 to 1/8 for keyed and other manually assembled pintles with locking nut.1/20 to 1/12 for pintle mounted with oil injection and hydraulic nut.

iv) Threads and nuts are to be in accordance with 3/5.9.4.

v) For rudders on horns with two pintles, as shown in 3-2-13/Figure 3b of theSteel Vessel Rules ,calculations are to include pintle bearing forces with the craft running ahead at the maximum

continuous rated shaft rpm and at the lightest operating draft.vi) The bearing allowable pressure is to be in accordance with Table 3/5.6.


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3/5.11.2 Diameter

The diameter of the pintles is not to be less than obtained from the following equation.

p p BK k d 1= mm (in.)

where

k 1 = 11.1 (34.7, 1.38)

B = bearing force, in kN (tf, Ltf), from 3-2-8/13.5 but not to be taken less than Bmin asspecified in Table 3/5.4

K p = material factor for the pintle, as defined in 3/5.1.2

TABLE 3/5.4 Minimum Bearing Force Bmin (2009)

Pintle Type B min Conventional two pintle rudder 0.5 C R Figure 3/A.2 lower pintle 0.5 C R Figure 3/A.3 main pintle C Rl a/l p*

main pintle C Rl a/l p*3-2-13/Figure 3 of theSteelVessel Rules upper pintle 0.25C R

* Bmin = C R where l a/l p 1

la, l p as described in 3-2-13/Figure 3 of theSteel Vessel Rules

3/5.11.3 Shear and Bearing Forces

The shear and bearing forces may be determined in accordance with Appendix 3/A, or by theequations given below.

a Spade Rudder

Bearing force at rudder carrier: P u =u

n M l

kN (tf, Ltf)

Bearing force at neck bearing: P n = C R + P u kN (tf, Ltf)

Shear force at neck bearing: F n = C R kN (tf, Ltf)

whereC R is as defined in 3/5.2 andl u is as defined in 3/5.5.3b.

b Balanced Rudder with Shoepiece Support

Bearing force at rudder carrier:u

nu

M P

l= kN (tf, Ltf)

Bearing force at neck bearing: P n =

++

+ p R

b

R

b

uu

C P l

l

ll

l

21 kN (tf Ltf)


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wherel

b = distance between the center of neck bearing support and the center ofshoepiece support, as shown in Figure 3/A.2

= l p + l r + l l l p = distance between bottom of rudder blade and center of support of neck

bearingl l = distance between top of rudder blade and center of support of neck

bearingBearing force at shoepiece: P p = C R + P u P n kN (tf, Ltf)

but not less than 0.5C R Shear force at neck bearing: F n = P n P u kN (tf, Ltf)whereC R is as defined in 3/5.2.

3/5.13 Supporting and Anti-Lifting Arrangements3/5.13.1 Rudder Stock and Pintle Bearings

a Bearing Surfaces. Bearing surfaces for rudder stocks, shafts and pintles are to meet thefollowing requirements:

i) The length/diameter ratio (l b/d l ) of the bearing surface is not to be greater than 1.2

ii) The projected area of the bearing surface ( Ab = d l l b) is not to be taken less than Abmin,

where

d l = outer diameter of the liner, in mm (in.)

l b = bearing length, in mm (in.)

Abmin =aq

P k 1 mm2 (in2)

k 1 = 1000 (2240)

P = bearing reaction force, in kN (tf, Ltf), as determined from Table 3/5.5

qa = allowable surface pressure, as indicated in Table 3/5.6, depending on bearingmaterial, in N/mm2 (kgf/mm2, psi)

TABLE 3/5.5 Bearing Reaction Force (2009)

P , Bearing Reaction Force Bearing Type kN (tf, Ltf)

Pintle bearings P = B as defined in 3/5.11Other bearings Calculation of P is to be submitted.

Guidelines for calculation can befound in Appendix 3/A


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TABLE 3/5.6 Bearing Pressure (2009)

qa

Bearing Material N/mm2 qa kgf/mm2 psi

lignum vitae 2.5 0.25 360white metal, oil lubricated 4.5 0.46 650Synthetic material with hardness between 60 and 70 Shore D* 5.5 0.56 800Steel, bronze and hot-pressed bronze-graphite materals 7.0 0.71 1000

Higher values than given in the table may be taken if they are verified by tests.

Stainless and wear-resistant steel in an approved combination with stock liner.

* Indentation hardness test at 23C and with 50% moisture, according to a recognized standard.Synthetic bearing materials to be of approved type.

b Bearing Clearance. With metal bearings clearance is not to be less thand b/1000 + 1.0 mm,(d b/1000 + 0.04 in.) on the diameter. If non-metallic bearing material is applied, the bearing clearance

is to be specially determined considering the materials swelling and thermal expansion properties.This clearance is in no case to be less than 1.5 mm (0.06 in.) on diameter or the bushingmanufacturers recommended clearance.For spade rudders with a rudder stock diameter of 400 mm (15.75 in.) or less, the clearances on thediameter are not to be less than given below:

Stock Diameter, mm (in.) Metallic Bushing, mm (in.) Synthetic Bushing (1) , mm (in.)

400 (15.75) 1.15 (0.045) 1.15 (0.045) + E (2) 300 (11.81) 0.85 (0.033) 0.85 (0.033) + E 200 (7.87) 0.78 (0.031) 0.78 (0.031) + E 100 (3.94) 0.75 (0.030) 0.75 (0.030) + E

Notes1 The bushing manufacturers recommended running clearance may be used as an alternative to

these clearances.

2 E = expansion allowance provided by bushing manufacturer, mm (in.).

3/5.13.2 Rudder Carrier

The weight of the rudder assembly is to be supported by a rudder carrier mounted on the hull structuredesigned for that purpose. At least half of the rudder carrier holding-down bolts are to be fitted bolts.Alternative means of preventing horizontal movement of the rudder carrier may be considered.

3/5.13.3 Anti-Lifting Devices

Means are to be provided to prevent accidental unshipping or undue movement of the rudder which maycause damage to the steering gear. There are to be at least two bolts in the joint of the anti-lifting ring.

3/5.15 Double Plate Rudder

3/5.15.1 Strength

The section modulus and web area of the rudder mainpiece are to be such that the stresses indicated inthe following Subparagraphs are not exceeded.

In calculating the section modulus of the rudder, the effective width of side plating is to be taken asnot greater than twice the athwartship dimension of the rudder. Welded or bolted cover plates on

access openings to pintles are not to be considered effective in determining the section modulus of therudder. Generous radii are to be provided at abrupt changes in section where there are stressconcentrations, including in way of openings and cover plates.


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Moments, shear forces and reaction forces are to be as given in 3/5.3.3 and 3/5.11.3.

a Clear of Cutouts

Bending stress b = K /Q N/mm2 (kgf /mm2, psi)

Shear stress = K /Q N/mm2 (kgf /mm2, psi)

Equivalent stress e =22 3 +b = K e /Q N/mm2 (kgf/mm2, psi)

where

SI units MKS units US units K 110 11.2 15,900

K 50 5.1 7,300

K e 120 12.2 17,400

Q = as defined in 3/6.1.1ab In way of Cutouts

Allowable stresses for determining the rudder strength in way of cutouts (see Figure 3/5.4) areas follows:

Bending stress b = K /Q N/mm2 (kgf /mm2, psi)

Shear stress = K /Q N/mm2 (kgf /mm2, psi)

Equivalent stress e =22 3 +b = K e /Q N/mm2 (kgf/mm2, psi)

where

SI units MKS units US units K 75 7.65 10,900

K 50 5.1 7,300

K e 100 10.2 14,500

Q = as defined in 3/6.1.1a


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FIGURE 3/5.4 (2009)

Z

6r 2

6r 1

6r 1

r 26r 2

X Note:r

1 = corner radius of rudder plate in way of

portable bolted inspection holer 2 = corner radius of rudder plate

I n w a y o

f c u

t o u

t s

r 1

The mainpiece of the rudder is to be formed by the rudder side plating (but not more than the effectivewidth indicated above) and vertical diaphragms extending the length of the rudder or the extension ofthe rudder stock or a combination of both.For spade rudders, the section modulus at the bottom of the rudder is not to be less than one-third therequired section modulus of the rudder at the top of the rudder or at the center of the lowest pintle.Where rudders have an unsymmetrical foil section (e.g., reaction rudder) details of the rudder are to

be submitted.Special attention is to be paid in design and construction of rudders with slender foil sections in thevicinity of their trailing edge (e.g., hollow foil sections, fishtail foil sections). Where the width of therudder blade at the aftermost vertical diaphragm is equal or less than 1/6 of the trailing edge lengthmeasured between the diaphragm and the trailing edge, vibration analysis of the rudder blade is alsoto be submitted for review.

3/5.15.2 Side, Top, and Bottom Plating

The plating thickness is not to be less than obtained from the following equation:

t = 0.0055 s ( ) AC k d k R /21 + Q + k 3 mm (in.)

wherek 1 = 1.0 (1.0, 0.305)k 2 = 0.1 (0.981, 10.7)k 3 = 2.5 (2.5, 0.1)d = summer loadline draft of the craft, in m (ft)C R = rudder force according to 3-2-8/3, in kN (tf, Ltf)

A = rudder area, in m2 (ft2) s = smaller unsupported dimension of plating, in mm (in.)b = greater unsupported dimension of plating, in mm (in.)

= 2)/(5.01.1 b s ; maximum 1.0 forb/ s 2.5


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Q = material factor for rudder plating, as defined in 3/6.1.1aThe thickness of the rudder side or bottom plating is to be at least 2 mm (0.08 in.) greater than thatrequired by 3/9.1.2a with p obtained from 3/8.6.1, for whichh is measured from the lower edge of the plate to the design waterline in displacement mode.

3/5.15.3 Diaphragm Plates

Vertical and horizontal diaphragms are to be fitted within the rudder, effectively attached to each otherand to the side plating. Vertical diaphragms are to be spaced approximately 1.5 times the spacing ofhorizontal diaphragms. Openings are in general not to be more than 0.5 times the depth of the web.The thickness of diaphragm plates is not to be less than 70% of the required rudder side plate thicknessor 8 mm (0.31 in.) whichever is greater. Openings in diaphragms are not to exceed one half their depth.

Welding is to be in accordance with Section 2-4-1 of the ABS Rules for Materials and Welding (Part 2) and Section 3/23 of this Guide. Where inaccessible for welding inside the rudder, it is recommendedthat diaphragms be fitted with flat bars and the side plating be connected to these flat bars bycontinuous welds or by 75 mm (3 in.) slot welds spaced at 150 mm (6 in.) centers. The slots are to befillet welded around the edge, and filled with a suitable compound.3/5.15.4 Watertightness

The rudder is to be watertight and is to be tested in accordance with Table/1/2.1.

3/5.17 Single Plate Rudder

3/5.17.1 Mainpiece Diameter

The mainpiece diameter is calculated according to 3/5.5.2. For spade rudders, the lower third may betapered down to 0.75 times stock diameter at the bottom of the rudder.

3/5.17.2 Blade Thickness

The blade thickness is not to be less than obtained from the following equation:

t b = 0.0015 sV R + 2.5 mm t b = 0.0015 sV R + 0.1 in.

where

s = spacing of stiffening arms, in mm (in.), not to exceed 1000 mm (39 in.)

V R = speed, as defined in 3/5.2.1

3/5.17.3 Arms

The thickness of the arms is not to be less than the blade thickness obtained in 3/5.17.2. The sectionmodulus of each set of arms about the axis of the rudder stock is not to be less than obtained from thefollowing equation:

SM = 0.0005 sC 12V 2 cm3 SM = 0.0000719 sC 12V 2 in3 where

C 1 = horizontal distance from the aft edge of the rudder to the centerline of the rudderstock, in m (ft)

Q = as defined in 3/6.1.1a

s, V R are defined in 3/5.17.2.

3/5.19 Shelled Rudder Blades

Rudder blades that are constructed out of cast resilient polymers or filled FRP shells are to have asolid metallic core that complies with the requirements for single plate rudders, see 3/5.17.


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APPENDIX A GUIDELINES FOR CALCULATING BENDING MOMENT AND SHEARFORCE IN RUDDERS AND RUDDER STOCKS

(Add new Subsections 3/A.3 and 3/A.5, as follows.)

3/A.3 Rudder Supported by Shoepiece

3/A.3.1 Shear Force, Bending Moment and Reaction Forces

Shear force, bending moment and reaction forces may be calculated according to the model given inFigure 3/A.2.

w R = rudder load per unit length

= R

RC l

kN/m (tf/m, Ltf/ft)

where

C R = rudder force, as defined in 3/5.2

k s = spring constant reflecting support of the shoepiece

= 3 s

s s I nl

kN/m (tf/m, Ltf/ft)

n s = 6.18 (0.630, 279)

I s = moment of inertia of shoepiece about the vertical axis, in cm4 (in4)

I u = moment of inertia of the rudder stock above the neck bearing, in cm4 (in4)

I l = moment of inertia of the rudder stock below the neck bearing, in cm4 (in4)

I R = moment of inertia of the rudder about the longitudinal axis, in cm4 (in4)

I p = moment of inertia of the pintle, in cm4 (in4)

l l , l s, l R and l u are dimensions as indicated in Figure 3/A.2, in m (ft).


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FIGURE 2Rudder Supported by Shoepiece

w Rl R

ll

lu

lb

l p

l s

k s

3/A.5 Rudder Supported by a Horn with One Pintle

3/A.5.1 Shear Force, Bending Moment and Reaction Forces

Shear force, bending moment and reaction forces are to be assessed by the simplified beam modelshown in Figure 3/A.3.

w R1 = rudder load per unit length above pintle

=1

1

R

RC l

kN/m (tf/m, Ltf/ft)

w R2 = rudder load per unit length below pintle

=2

2

R

RC l

kN/m (tf/m, Ltf/ft)

where

C R1 = rudder force, as defined in 3/5.2.2

C R2 = rudder force, as defined in 3/5.2.2


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k h = spring constant reflecting support of the horn

=

2

23

1

an

et

s

I n t

hi

i

hb

h

l

l

+

kN/m (tf/m, Ltf/ft)

nb = 4.75 (0.485, 215)

nt = 3.17 (0.323, 143)

a = mean area enclosed by the outside lines of the rudder horn, in cm2 (in2)

si = the girth length of each segment of the horn of thicknesst i, in cm (in.)

t i = the thickness of each segment of horn outer shell of length s i, in cm (in.)

I h = moment of inertia of horn section atl

h about the longitudinal axis, in cm4

(in4)

e, l h, l R1 and l R2 are dimensions as indicated in Figure 3/A.3, in m (ft).

FIGURE 3Rudder Supported by a Horn with One Pintle (2009)

2

ll

lu

l R1

lh

w R1

w R2

lh

e k hl R2


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PART 4 MACHINERY EQUIPMENT AND SYSTEMS

SECTION 1 CONDITIONS OF CLASSIFICATION OF MACHINERY

4/1.11 Machinery Plans & Data(Add two new items to 4/1.11 Fire Safety, as follows.)

Fire SafetyArrangement and details of control station for emergency closing of openings and stoppingmachineryDetails and location of firemans outfitsDetails of fire extinguishing appliancesFire control plans (see 4/9.1.7)Plans of the following systems:

Fire main systemFoam smothering systemFire detection systemsFixed gas extinguishing systemFixed water spraying system

Other fire extinguishing arrangements(2010) The most severe service condition for the operation of the emergency fire pump (e.g.lightest draft as shown in Trim and Stability Booklet, etc.)(2010) Calculations and pump data demonstrating that the emergency fire pump system canmeet the operational requirements specified in 4/9.3.2 with the proposed pump location and piping arrangements (e.g. adequate suction lift, discharge pressure, capacity, etc.) at the mostsevere service condition


SECTION 5 ELECTRICAL INSTALLATIONS

PART A SYSTEMS

4/5A2 Craft Service Main Source of Power

4/5A2.1 Power Supply by Generator(Revise Subparagraphs 4/5A2.1.2 and 4/5A2.1.3, as follows.)

4/5A2.1.2 Capacity of Generators (2010)

The capacity of the generating sets is to be such that in the event of any one generating set beingstopped, it will still be possible without recourse to the emergency source of power to supply thoseservices necessary to provide normal operational conditions of propulsion and safety, preservation ofthe cargo and minimum comfortable conditions of habitability, which are to include at least adequateservices for cooking, heating, domestic refrigeration, mechanical ventilation, sanitary and fresh water.See also 4-6-2/3.1.6. In addition, the generating sets are to be such that with any one generator or its primary source of power out of operation, the remaining generating sets are capable of providing theelectrical services necessary to start the main propulsion plant in conjunction with other machinery, asappropriate, from a dead ship condition, as defined in 4-1-1/13.21, within thirty minutes of the blackout. See also 4-6-2/3.1.3.


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4/5A2.1.3 Starting from Dead Craft Condition (2010)

The generating sets are to be such that with any one generator or its primary source of power out ofoperation, the remaining generating sets are capable of providing the electrical services necessary tostart the main propulsion plant from a dead craft condition. The emergency source of electrical powermay be used for the purpose of starting from a dead craft condition if its capacity either alone orcombined with that of any other available source of electrical power is sufficient to provide at thesame time those services required to be supplied by 4/5A3.3.2 to 4/5A3.3.3.

4/5A9 Manually Operated Alarms

(Revise Paragraph 4/5A9.1, as follows.)

4/5A9.1 General Emergency Alarm System (2010)

Each craft over 100 GT is to be fitted with a general emergency alarm. The system is to be

supplemented by either a public address system, in accordance with 4-6-2/15.9, or other suitablemeans of communication. Any entertainment sound system is to be automatically turned off when thegeneral emergency alarm is activated. For passenger vessels, see also 5/13.13 and 5/13.15 of theGuide for Building and Classing Passenger Vessels .

a The general emergency alarm system is to be capable of sounding the general emergencyalarm signal consisting of seven or more short blasts followed by one long blast on the crafts whistleor siren and additionally on an electrically operated bell or klaxon or other equivalent warning system,which is to be powered from the crafts main supply and the emergency source of electrical powerrequired by 4/5A3, as appropriate.

b There are to be not less than two sources of power supply for the electrical equipment used inthe operation of the General Emergency Alarm System, one of which is to be from the emergencyswitchboard and the other from the main switchboard. The supply is to be provided by separatefeeders reserved solely for that purpose. Such feeders are to run to an automatic change-over switchsituated in, or adjacent to, the main general emergency alarm control panel.

c An alarm is to be provided to indicate when there is a loss of power in any one of the feedersrequired by 4/5A9.1b.

d As an alternative to two feeders as described in 4/5A9.1b, a battery may be considered as oneof the required sources, provided the battery has the capacity of at least 30 minutes of continuousoperation for alarming and 18 hours in standby. A low voltage alarm for the battery and the batterycharger output is to be provided. The battery charger is to be supplied from the emergency switchboard.

e The system is to be capable of operation from the operating compartment and, except for

crafts whistle, also from other strategic points. The system is to be audible throughout all of theaccommodation and normal crew working spaces and open decks, and its sound pressure level is to beat least 10 dB(A) above ambient noise levels under way in normal cruise operation. The alarm is tocontinue to function after it has been triggered until it is manually turned off or is temporarilyinterrupted by a message on the public address system.


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4/5A10 Fire Protection and Fire Detection Systems

4/5A10.1 Emergency Stop

(Revise Subparagraph 4/5A10.1.2, as follows.)

4/5A10.1.2 Other Auxiliaries (2010)

See 4/6.43.3 and 4/9.5.3 for emergency tripping and emergency stop for other auxiliaries, such asforced and induced draft fans, fuel oil units, lubricating oil service pumps, thermal oil circulating pumps and oil separators (purifiers).


SECTION 5 ELECTRICAL INSTALLATIONS

PART C MACHINERY AND EQUIPMENT

4/5C4 Switchboards, Distribution Boards, Controllers, etc.

4/5C4.11 Bus Bars, Wiring and Contacts

(Revise Subparagraph 4/5C4.11.7, as follows.)

4/5C4.11.7 Terminals (2010)

Terminals or terminal rows for systems of different voltages are to be clearly separated from eachother. The rated voltage is to be clearly indicated at least once for each group of terminals which have been separated from the terminals with other voltage ratings. Terminals with different voltage ratings,each not exceeding 50 V DC or 50 V AC may be grouped together. Each terminal is to have anameplate indicating the circuit designation.


SECTION 6 PUMPS AND PIPING SYSTEMS

4/6.43 Vent Pipes

(Revise first paragraph of Paragraph 4/6.43.5, as follows.)

4/6.43.5 Vent Outlets (2010)

All vent and overflow pipes terminating in the weather are to be fitted with return bends (gooseneck),or equivalent, and the vent outlet is to be provided with an automatic means of closure, [i.e., closeautomatically upon submergence (e.g., ball float or equivalent)], complying with 4/6.43.5c.


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4/6.71 Fixed Oxygen-Acetylene Installations

(Revise Paragraph 4/6.71.2, as follows.)

4/6.71.2 Piping and Fittings

a General. The wall thickness of piping between cylinders and pressure regulators is to be inaccordance with 4/6.13.6.

b Materials. Materials for piping on the high pressure side of the regulators are to be steel foracetylene and steel or copper for oxygen. All piping is to be seamless. Copper or copper alloyscontaining more than 65% copper are not to be used in connection with acetylene.

c Installation. Where two or more cylinders are connected to a manifold, the supply pipe between each cylinder and the manifold is to be fitted with a non return valve. Piping and fittings onthe low pressure side of the regulators are to be in accordance with above requirements except thatseamless steel pipes of at least standard wall thickness may be used. Except for the cylinder manifolds,acetylene is not to be piped at a pressure in excess of 1.0 bar (1.0 kgf/cm2, 15 psi). All piping on thelow pressure side is to have all joints welded. Branch lines are not to run through unventilated spacesor accommodation spaces.

d Flexible Hoses (2010). Flexible hoses used to connect oxygen or acetylene gas cylinders to afixed piping system or manifold are to comply with an acceptable standard and be suitable for theintended pressure and service. Further, the internal surface of a hose used to connect an acetylene tankis to be of a material that is resistant to acetone and dimethylformamide decomposition. Where aflexible hose is connected from an oxygen cylinder to the piping system or manifold directly (i.e. nointervening pressure regulator), the internal liner of the oxygen hose is to be of a material that has anauto ignition temperature of not less than 400C (752F) in oxygen.

e Testing. The system is to be tested in accordance with 4/6.9.7. Note: Prior to installation of oxygen and acetylene pipe lines, all piping and fittings are to be thoroughly cleaned with a

suitable solution, which will not react with oxygen, to remove all grease, oil and dirt. Piping should be thoroughly blown out after assembly to remove foreign materials. For oxygen piping, oil-free air or oil-free nitrogen should be used. For acetylene, air or inert gas may be used.


SECTION 7 PROPULSION SHAFTING, PROPELLERS, WATERJETS AND LIFTDEVICES

4/7.5 Tailshaft Liners


4/7.5.1 Thickness at Bearings (2010)

a Bronze Liner. The thickness of bronze liners to be fitted to tail shafts or tube shafts is not to be less than that given by the following equation:

t = T /25 + 5.1 mm t = T /25 + 0.2 in.where

t = thickness of liner, in mm (in.)

T = required diameter of tail shaft, in mm (in.)


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b Stainless Steel Liner. The thickness of stainless steel liners to be fitted to tail shafts or tubeshafts is not to be less than one-half that required for bronze liners or 6.5 mm (0.25 inches), whicheveris greater.


4/7.5.13 Stainless Steel Cladding (2010)

Stainless steel cladding of shafts is to be carried out in accordance with an approved procedure. SeeAppendix, Section 11, Guide for Repair and Cladding of Shafts of the ABS Rules for Survey AfterConstruction (Part 7) .

4/7.16 Propulsion Shaft Alignment and Vibrations

4/7.16.2 Craft 61 m (200 ft) in Length and Over

(Add new Subparagraph 4/7.16.2e, as follows.)

e Cast Resin Chocks (2010) . Resin chocks and their installation are to comply with therequirements in 4-3-2/11.1.2 of theSteel Vessel Rules :


SECTION 8 STEERING

4/8.2 Materials


4/8.2.2 Material Testing (2010)

Material tests for forged, welded or seamless steel parts (including the internal components) of rudderactuators that are under 150 mm (6 in.) in internal diameter need not be carried out in the presence ofthe Surveyor. Such parts are to comply with the requirements of 2/2 or such other appropriate materialspecification as may be approved in connection with a particular design and will be accepted on the basis of a presentation of mill certificates to the Surveyor for verification.

4/8.3 Design

4/8.3.3 Tiller

(Add new Item 4/8.3.3.9, as follows.)

9 Bolted Hub (2010) . Split or semi-circular tiller or quadrant hubs assembled by bolting are to have bolts on each side having a total cross-sectional area not less thanthat given below (use a consistent system of units):

s

b

K K

LS

3

3196.0


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where

L3 = distance between the center of the bolts and the center of the rudder stock

K b = material factor of bolt (see 3/5.1.2)

Other symbols are as defined above.The thickness of the bolting flange is not to be less than the minimum required diameter ofthe bolt.


SECTION 9 FIRE EXTINGUISHING SYSTEMS

4/9.1 General

(Add new Paragraph 4/9.1.8, as follows.)

4/9.1.8 Additional Fixed Fire Fighting Systems (2010)

Where a fixed fire extinguishing system not required by Section 4/9 is installed, such system is tomeet the applicable requirements of 4/9.25 and is to be submitted for approval.

4/9.3 Fire Pumps, Fire Main, Hydrants and Hoses

(Revise Paragraph 4/9.3.5, as follows.)4/9.3.5 Additional Fixed Fire Fighting Systems (2010)

a General. Fire hoses are to be of a type certified by a competent independent testinglaboratory as being constructed of non-perishable material to a recognized standard. The hoses are to be sufficient in length to project a jet of water to any of the spaces in which they may be required to be used.Fire hoses are to have a length of at least 10 m (33 ft), but not more than:

15 m (50 ft) in machinery spaces; 20 m (66 ft) in other spaces and open decks; and

25 m (82 ft) for open deck on vessels with a maximum breath in excess of 30 m (98 ft)Each hose is to have a nozzle and the necessary couplings. Fire hoses together with any necessaryfittings and tools are to be kept ready for use in conspicuous positions near the hydrants.

b Diameter. For vessels less than 500 gross tons, hoses are not to have a diameter greater than38 mm (1.5 in.). Hoses for craft under 20 m (65 ft) in length may be of a good commercial gradehaving a diameter of not less than 16 mm (5/8 in.) and are to be have a minimum test pressure of 10.3 bar (10.5 kgf/cm2 , 150 psi) and a minimum burst pressure of 31.0 bar (31.6 kgf/cm2 , 450 psi).

c Number of Fire Hoses. In vessels of 1,000 gross tonnage and upwards, the number of firehoses to be provided is to be at least one for each 30 m (100 ft) length of the vessel and one spare, butin no case less than five in all. This number does not include any hoses required in any engine or

boiler room.


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In vessels of less than 1,000 gross tonnage, the number of fire hoses to be provided is to be at leastone for each 30 m (100 ft) length of the vessel and one spare. However, the number of hoses is to bein no case less than three.Unless one hose and nozzle is provided for each hydrant in the vessel, there are to be completeinterchangeability of hose couplings and nozzles.

4/9.5 Means for Closing of Openings, Stopping of Machinery and OilContainment


4/9.5.3 Other Auxiliaries (2010)

Machinery driving forced- and induced-draft fans, oil-fuel transfer pumps, oil-fuel unit pumps andother similar fuel pumps, fired equipment such as an incinerator, lubricating oil service pumps,

thermal oil circulating pumps and oil separators (purifiers) are to be fitted with remote shutdownssituated outside of the spaces concerned so that they may be stopped in the event of a fire arising inthe space. This need not apply to oily water separators. See 4/5A10.1.2.In addition to the remote shutdowns required above, a means to shutdown the equipment is to be provided within the space itself.


SECTION 11 SHIPBOARD CONTROL AND MONITORING SYSTEMS(Revise Item B4 and Note 6 of Table 4/11.5, as follows.)

TABLE 4/11.5 Monitoring of Propulsion Machinery Medium/High (Trunk Piston) SpeedDiesel Engines (2010)

Item (11) Alarm (1) Display

Automatic Startof Required

Standby Vital Auxiliary Pump

with Alarm (1) Remarks (12)

Lube OilSystem

B4 (2010) Oil mist in crankcase, mist

concentration high; or bearing temperature high; oralternative arrangements

x Automatic engine

shutdown(6)

Notes:6 (2010) For engines having a power of 2250 kW (3000 hp) and above or having a cylinder bore of more than 300

mm (11.8 in.).

Single sensor having two independent outputs for initiating alarm and for shutdown will satisfy independence ofalarm and shutdown.

See 4-2-1/7.2 of the Rules for Building and Classing Steel Vessels .


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(Revise Item D1 and Note 2 of Table 4/11.5, as follows.)

TABLE 4/11.8 Monitoring of Auxiliary Prime-movers and Electrical Generators (2010)

Item Alarm(1)

Display Remarks

DieselEngine Crankcase

D1 (2010) Oil mist in crankcase, mistconcentration high; or bearing temperature high; oralternative arrangements

x Automatic engine shutdown(2)

Notes:2 (2010) For engines having a power of 2250 kW (3000 hp) and above or having a cylinder bore more than 300 mm

(11.8 in.).

Single sensor having two independent outputs for initiating alarm and for initiating alarm and for shutdown willsatisfy independence of alarm and shutdown.

See 4-2-1/7.2 of the Rules for Building and Classing Steel Vessels .

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