Tribology Handbook 2 2010 Part 7 pot

B17 Piston rings NON METALLIC PISTON RINGS Metallic piston rings require lubrication for satisfactory applications, piston rings can be made from self- operation. There are, however, many applications where lubricating materials. These materials can also be used in lubricants would be considered a contaminant or even a lubricated applications where there is a risk of lubricant fire hazard, e.g. in food-processing equipment. For these breakdown. Ring materials Table 17.5 Typical properties of ring materials Malarial Tensile strength MN/~~ SpeciJic gravity Typical coef$cients of expansion x 1 O-~/OC Carbon-filled PTFE 10 2.05 55 Glass-filled PTFE 17 2.26 80 GraphitelMoS2 filled PTFE 20 2.20 115 Bronze-filled PTFE 13 3.90 I18 Resin-bonded PTFE 29 1.75 30 Resin-bonded fabric 110 1.36 Carbon 43 1.8 43 Resin-bonded carbon 20 1.9 20 * Material is anisotropic, thus the lower expansion is parallel to, and the alternative figure is normal to, the plane of pressing. Table 17.6 Suggested operating conditions for various materials Maximum Maximum Average Terminal pressure speed temp. humidiQ bars mls "C Material coejjicient Minimal of friction p,p,m, lubrication (4) Matrix Filler PTFE Carbon 200 6.0 250 0.1/0.15 3 Very good 0.1/0.15 3 Very good Glass 200 6.0 200 ~ ~ ~~ 0.12/0.18 3 Very good Graphite/MoS? 200 6.0 200 Bronze 100 4.0 200 0.15/0.2 40 Good 0.15 10 Very good Resin-bonded PTFE 200 4.0 200 Resin-bonded fabric Carbon ~ ~~ 100 3.0 150 0.15/0.2 40 Poor 60 3.8 350 0.2/0.25 40 Poor Resin-bonded carbon 100 4.5 180 0.2 40 Poor Ring design Table 17.7 Preferred number of rings ~~ ~~~~~~ Differential pressure bars 0-9 10-14 15-24 25-29 30-49 50-99 100-200 Minimum number of nngs 2 3 4 5 6 7 8 B17.6 Piston rings B17 Table 17.8 Suggested sizes of rings GTOOVE side Piston ring Units Cylinder diameter (b) clearance Axial width Radial thickness ( C) C = 0.025 X axial width Millimetres 2575 3-5 3-6 76150 5-10 5-10 15 1-230 6-12 G12 (N.B Groove 230-400 10-19 10-19 tolerance H7) ~~ ~~ 400-800 12-25 12-25 - Inches 1-3 0.125-0.187 0.125-0.218 3-6 0.187-0.375 0.1874.437 ~ ___~ 6-9 0.250-0.500 0.250-0.500 9-16 0.375-0.750 0.3 75-0.750 16-30 0.500-1.000 0.500-1.000 Table 17.9 Types of joints Butt Scarf Lap or step Suitable for all pressures Suitable for all pressures Not recommended where pressure differential exceeds 10 atmospheres Circumferential clearance (S) S = T X D X aP x T where D = cylinder diameter, ap = Coeff. of expansion of piston ring T = Operating temperature material, Cylinder materials and finishes Table 17.10 Typical cylinder materials ~ ~~ __________ ~ Material ryPe Remarks Cast iron IS0 R185 220 grade Suitable only for continuous operation Ni-Resist IS0 2892 AUS101. ASTM A436/1 Preferred to cast iron-less danger of corrosion Stainless steel IS0 683/1 316816. AIS1 316 Used for machines where long shutdowns occur Meehanite cast iron CR or CRS Similar to Ni-Resist A suitable surfface finish for these cylinder liners is 0.4 to 0.6 pm R, or 2.4 to 3.6 prn B 17.7 B18 Cylinders and liners MATERIALS AND DESIGN Table 18.1 Choice of materials for cylinders and cylinder liners Material Commenf Block Liner Surjacejnish and treatment I.C. Monobloc Most petrol engines. Grey C.1. (low - Simplest and cheapest Most applications use an engines Some oil engines phosphorus) method of building untreated cross-hatched (‘siamesed’ mass-production honed finish-See Note 3 cheaper and low For greater scuff resistance of specific power engines or where alloy (high tion in weight but C.I. a phosphate treatment space is at a premium) cylinders used for engines Gives maximum reduc- - Aluminium silicon) poses special problems can be used. For greater Aluminium with in material compati- wear resistance bores may be nickel plate bility with mating hardened on surface, containing component, i.e. through- or zone-hardened, silicon piston and rings or hard chromium-plated on carbide particles cast iron or steel liner. Sur- face porosity (by reverse Dry liner Oil engines and Grey C.I. (low Grey C.I. (low-to- Liner normally pressed- plating) is necessary with petrol engines phosphorus) medium phos- in but may be slip fit. chromium Plating to give phorus) Much improved wear, scuff resistance. Porous coat- can pose cooling pro- blems. Used for engine reconditioning in con carbide impregnation monobloc system ings aid oil retention reduc- ing scuffing and wear. sili- can be used to combat bore polishing. Aluminium Grey C.I. (low-to- Liner normally cast-in or alloy medium phos- pressed-in phorus) Wet liner High-performance Grey C.I. Grey ‘2.1. (low-to- Wet liner requirement for petrol and most oil medium phos- long life, good cooling engines phorus) Grey and ease of mainte- C.I. with silicon nance carbide impregnation iron Austenitic cast Aluminium alloys (high silicon) require special surface finish to allow free silicon to stand out from the matrix. Nickel plate with silicon carbide particles is the most common solution for aluminium bores. Some cheaper alumi- nium alloys may be used for ‘throw-away’ engines. Piston skirts may be electroplated with iron or chromium. Aluminium Grey C.I. High-performance alloy austenitic C.I. petrol engines to reduce Costs rise significantly from the Aluminium weight basic monobloc cast-iron cy- alloy (high silicon) nickel plate with technical requirements containing silicon carbide particles linder block. Care must be taken to ensure the mini- Aluminium with mum specification consistent Monobloc Small size and low Grey C.I. (low - As in i.c. engines As in i.c. engines except where pressors pressure (up to phosphorus) plastics piston rings are used in which case honed ‘mirror- Com- 34 in dia. and 100 psi) finish’ is desirable Wet liner Heavy duty long life As in i.c. engines As in i.c. engines high reliability units of all sizes and ope- rating pressures Hydraulic To suit - Grey cast iron Material depends on en- Fine turned or honed to mirror actuators design Bronze vironmental require- finish and fluid require- Aluminium ments of pressure, piston ments alloy duty, reliability and Hardened steel bores usually Pumps Steel fluid in use ground or lapped B18.1 Cylinders and liners 918 Table 18.2 Cylinderk ylinder liner tolerances Ovality Concentrin'ty mm mm Monoblocs 0.025 FIM max Press fit dry type cylinder liners 0.150 FIM max 0.150 FIM max Slip fit dry type cylinder liners* 0.050 FIM max 0.100 FIM max Wet type cylinder liners* 0.025 FIM max 0.100 FIM max * It is also vital that the flange be parallel and square to the major axis of the liner within 0.050 mm. Table 18.3 Interference fHs I Cast iron lincrs in cast iron blocks Diameter 2 Aluminium liners or Grcy cast iron in austenitic iron liners aluminium blocks in aluminium blocks mm mm mm up to 40 0.025 min over 40 to 50 0.040 min over 50 to 75 0.050 rnin over 75 to 100 0.075 min over 100 to 155 0.100min 0.075 rnin 0.100 min 0.1 15 min 0.125 rnin 0.140 min Nota: 1. Choice of construction and material is dependent on market being catered for: i.e. cost, power output or delivery requirement, life requirement, size and in- tended application. 2. Choice of material is also dependent on material used for pistons and rings and on any surface coatings given to these. Also, but to a lesser extent, on the surface treatment. 3. Honing specifications generally satisfactory; lies in the range 20 to 40 micro-inches, with a horizontal included angle of cross-hatch of 30/60" and a 60% plateau area. Surfaces must be free from folds, tears, burrs and burnished areas (see illustration). Suitable surface con- ditions can be most easily accomplished with silicon carbide hones. Diamond hones can be used but are best confined to roughing-cuts. Finishing can then be per- formed with silicon carbide honing stones or for more critical applications with silicon carbide particles in a soft matrix such as cork. Control of production tools and machines is vital for satisfactory performance in series production. 4. Sealing of wet liners is of great importance-see BS 4518 for Sealing Rings. Proprietary sealant/adhesive materials are available for assisting in sealing and in fixing liners. B18.2 E318 Winders and liners Table 18.4 Materials, compositions and properties Type Typical composition (Yo) (Remainder is Fe) Typical properties C Si S P Mn Ni Cr Others Coeff. of thermal expansion U. T.S BHN 20"-200"c Sand-cast blocks and barrels 3.3 2.1 0.1 0.15 0.6 0.3 0.2 11.0 X 10-6/oC.0 X 10 220MN/m2 200 Sand-cast liners 3.3 1.8 0.1 0.25 0.8 - 0.4 11.0 x 10-6/0c 230MN/m2 200 ~ ~~~~ ~ Centrifugally-cast grey iron 3.4 2.3 0.06 0.5 08 - 0.4 11.0 x 10-6/"c 260MN/m2 250 liners Centrifugally-cast alloy iron 3.3 2.2 0.06 0.2 0.8 - 0.4 Ni and Cu 10.5 X 10-6/oC 320MN/m2 280 liners 0.5-1.5 MoIVa 0.4 Austenitic iron liners 2.9 2.0 0.06 0.3 0.8 14.0 2.0 Cu 7.0 19.3 X 10-6/"C 190MN/m2 180 Table 18.5 Microstructures required Trpe Microstructure Sand-cast blocks and barrels Flake graphite, pearlitic matrix, no free carbides, phosphide eutectic network increases with phosphorus content, minimum of free ferrite desirable to minimise possibility of scuffing but less important with increasing phosphide Sand-cast liners As for sand cast but with finer graphite tending towards rosette or undercooled. Matrix martensitic/bainitic if linear hardened and tempered Compact graphite or quasi-flakes, pearlitic matrix, islands of wear-resistant alloy carbides distributed throughout (approx. 5% by volume) matrix. Phosphide exists as ternary eutectic with carbides. Minimum of free ferrite ideal, but not important in presence of carbides Centrifugally-cast grey iron liners Centrifugally-cast alloy iron liners ~ ~~~~ Uniformly distributed fine flake graphite along with some undercooled graphite (ASTM Types A along with some D and E, Sizes 5-8. Fine-grained cored austenite matrix. Complex carbides and ternary phosphide eutectic are present in controlled amounts in a broken, non-continuous network Austenitic iron liners B18.3 Selection of seals B19 BASIC SEAL TYPES AND THEIR CHARACTERISTICS Dynamic seal Sealing takes place between surfaces in sliding contact or narrowly separated. Static seal1 Sealing takes place between surfaces which do not move relative to each other. Pseudo-static seal Limited relative motion is possible at the sealing surfaces, or the seal itself allows limited motion; e.g. swivel couplings for pipes, flexible diaphragms. Exclusion seal A device to restrict access of dirt, etc., to a system, often used in conjunction with a dynamic seal. Table 19.1 Characteristics of dynamic seals Contact seals Clearance seals Sealing interface Surfaces loaded together: Predetermined separation (i) (ii) Hydrodynamic operation (normal loads, speeds and viscosities) Boundary lubrication (high loads, low speeds, low viscosities) LOAD FLUID FILM (a) I MOLECULAR PRESET FILM (b) GAP b) 6) (ii) Leakage Low to very low or virtually zero As (i) High, except for viscoseal and centrifugal seal at design optimum - Friction Moderate High Low Life Moderate to good Short Indefinite ~~ ~~ Reliability Moderate to good Poor Good Table 19.2 Types of dynamic and static seals Dynamic seals Contact seals Clearance seals Static seals Rotary RecipracatoT oscillatory Rotary Reciprocatory Lip seal (Figure 19.1) ‘U’ ring, etc. (Figure 19.4) Labyrintht (Figure Labyrinth7 (Figure Bonded fibre sheet Mechanical seal (Figure Chevron (Figure 19.5) 19.10a) 19.10a) Spiral wound gasket 19.2) ‘0’ ring (Figure 19.6) Viscoseal (Figure 19.10b) Fixed bushing (Figure Elastomeric gasket Packed gland (Figure Lobed ‘0’ ring (Figure Fixed bushing (Figure 19.10d) Piastic gasket 19.3) 19.7) 19.lOd) Floating bushing (Figure ‘0’ ring* Coaxial PTFE seal Floating bushing (Figure 19. l0e) Sealant, setting Felt ring (Figure 19.8) 19.10e) Sealant, non-setting Packed gland (Figure Centrifugal seal (Figure ‘0’ ring Piston ring Polymeric bushing Pipe coupling Bellows (Figure 19.9) (Figure 19.101) Bellows Diaphragm 19.3) 19.1Oc) Inflatable gasket * Only for very slow speeds. t Usually for steam or gas. B19.1 619 Selection of seals RUBBER ,BONFfsEMETAL CASE \ ATMOSPHERIC SIDE - ARTER SPRING \ SEALING CONTACT (0.25- 1.0rnm) Figure 19.1 Rotary lip seal PUMP ,ADJUf:: ENT HOUSING I ATMOSPHERIC ROTATING OR RECIPROCATING PACKING SHAFf Figure 19.3 Packed gland Figure 19.6 ‘0‘ ring seal on control valve spool PUMP SEAL FACES / ;”’ RING HOUSING LAMPING FLANGE STATIONARY SEALING HEAD \ I ROTATING SHAFT GASKET Figure 19.2 Mechanical seal PISTON SEAL ROD SEAL \ I Figure 19.4 Square-backed ’U’ seals as piston and rod seals in a hydraulic cylinder - Figure 19.5 Chevron seal with shaped support rings LOBED ‘0’ RING Figure 19.7 Lobed ‘0 ring 0 RING PTFE - Figure 19.8 Coaxial PTFE seal (a1 (b) Figure 19.9 Metal bellows: (a) formed; (b) welded B19.2 Selection of seals B19 (di (e) (f) Figure 19.10 Examples of clearance seals: (a) labyrinth; (b) viscoseal; IC) centrifugal seal; (d) fixed bushing; (e) floating bushing; (f) polymeric-bushing seal Multiple seals One seal or several in series may be used, depending on the severity of the application. Table 19.3 shows six basic dynamic sealing problems where two fluids have to be separated. Since contact seals rely on the sealed fluids for lubrication of the sliding parts it is essential that the seal(s) chosen should be exposed to a suitable lubricating liquid. Where thus is not already so, a second seal enclos- ing a suitable ‘buffer’ liquid must be used Multiple seals are also used where the pressure is so large that It must be broken down in stages to comply with the pressure limits of the individual seals, or where severe limitations on contamination exist. Table 19.3 lists the procedures for dealing with these various situations. Where a buffer fluid is used, care should be taken to ensure proper pressure control, especially when exposed to temperature variation. The pressure drop across successive seals will not be identical unless positive control is provided. Terminodolg y: BUFFER FLUID Figure 19.11 Multiple seals, with buffer fluid ‘Tandem seals’ multiple seals facing same direction, used to stage the pressure drop of the system. Inter-stage pressures progressively lower than sealed pressure. pair of seals facing opposite directions, used to control escape of hazardous or toxic sealed fluid to environment, or to permit liquid lubrication of the inner seal. The buffer pressure is normally higher than the sealed pressure. ‘Double seals’ B19.3 BI9 Selection of seals SEAL SELECTION Table 79.3 The use of dynamic contact seals in the six dynamic sealing situations Con&uration (see diagram) Multiple seal Satisfactory unless: (i) no contamination permissible 64 IPl - P21 large (iii) liquids both poor lubricants (in) abrasive present Buffer fluid = gas or vacuum: pB >pi, p2 or pB <<pi, p2 Buffer fluid = liquid 1 or 2: Buffer fluid = good lubricant: pe >pi, p2 Buffer fluid = clean liquid: pB p~ > PI or p2, subject to abrasive location (PI + p2)/2 Satisfactory unless: (i) no contamination permissible Buffer fluid = gas or vacuum: p~ > p1 or pB > p2 or pB > pl, p2 or pB <PI, (4 IPI - P21 large P2 (zii) the liquid is a poor lubricant Buffer fluid = liquid: PB @I + p2)/2 (iv) abrasive present Buffer fluid = good lubricant: p~ >pi, p2 Buffer fluid = clean liquid: p~ > PI or p2, subject to abrasive location (c) Satisfactory unless: Buffer fluid = compatible (i) no contamination of vacuum liquid or gas; alternatively permissible use clearance seal(s) and (4 PZ * PZ evacuate buffer zone PB a PI (iii) the liquid is a poor lubricant (iv) abrasive present in liquid Buffer fluid = clean liquid: pB >pi (4 Unsatisfactory Buffer fluid = compatible liquid lubricant: PB>PI,P2 (e) Unsatisfactory Buffer fluid = compatible liquid lubricant: PB>Pl (r) Unsatisfactory Buffer liquid = compatible PB>PI>P2 liquid lubricant: '1 (e) B19.4 u - VACUUM 1 n VACUUM 2 Selection of seals 619 Check-Uist for seal selection Ternjmature (s'ee Figure 19.12): seals containing rubber, natural filbres or plastic (which includes many face seals) may have severe temperature limitations, depending on the material, for example: Natural rubber -50 to +80"C Nitrile rubber -40 to +I30 Fluorocarbon rubber -40 to +200 Perfluorocarbon rubber -10 to +300 PTFE, plastic -100 to +280 At low temperatures, certain of the fluoroelastomers may become less 'rubbery' and may seal less well at high pressure. Speed (see Figure 19.13) Pressure (see Figure 19.13) Sire (see Figure 19.14) Leakage (see Figure 19.15) After making an initial choice of a suitable type of seal, the section of this handbook which relates to that type of sealshould be studied. Discussion with seal manufacturers is also recommended. Fluid compatibility: check all materials which may be ex- posed to the fluid, especially rubbers. Abrasion resistance: harder sliding contact materials are usually better but it is preferable to keep abrasives away from the seal if at all possible, for example by flushing with a clean fluid. Polyurethane and natural rubber are particularly abra- sion resistant polymers. Where low friction is also necess- ary filled PTFE may be considered. Vibration: should be minimised, but rubber seals are likely to function better than hard seals. 1200 1100 I000 u g 900 ii 800 3 a 2 700 W In IL 600 0 $ 500 Q 400 a 300 200 100 0 W 2 E w MECHANICAL W c figure 19.12 Approximate upper temperature limits for seals B19.5 [...]... - TURBUL ~ w I 6 2 rY 3 lo2; 3 L 8 7 0 0 5 u 5 z 4 0 3 J 0 z u z 2 0 10 ; 8 7 6 s 4 3 2 1.0 1 10 2 2 3 4 5 6 7 891 10’ lo3 D!MENS!ONLESS 1o4 2 3 4 5 6 7 8 9 1 lo5 PRESSURE, Figure 22 .3 Leakage flow of an incompressible fluid through an axial bush at various shaft eccentricities B 22. 2 yrinths, brush seals and throttling bushes B 22 1of 1O F L m 0 I 104 E, Q L u ) l - a n Y ,d Q 103 1o2 1 0 1 10 10 0... manufacture Housing Up to 100 mm (4in) 20 . 025 mm (0,001 in) 100- 175 mm (4 -7 in) 20 .0 37 mm (0.0015 in) Over 175 mm (7 in) k0.05 mm (0.0 02 in) Shaft Up to 50 mm (2 in) f0. 025 mm 50-100 mm (2- 4 in) 20 .0 37 mm 100 -20 0 mm' (4-8 in) k0.05 mm Over 20 0 mm (8 in) k0. 125 mm Temperature range Eccentricity ~ Surface finish Machining tolerances (0.001 in) (0.0015 in) (0.0 02 in) (0.005 in) Sealing dirt and grit 1... as shown in Figure 21 .1 1.4 100 0 20 0 400 300 1.3 1 .2 20 1 1.1 4 1.0 ‘ 0 , 1 50 100 I I 150 ( rev/s1 75 3 I 20 0 I 25 0 rnm Figure 21 .2 c - - _I TYPICAL THROWERS 2 Scale details of some well-proven throwers are given in Figures 21 .3, 21 .4 and 21 .5 Relevant values of Do/D for the originals are given in each case The application of each type may be assessed from Figure 21 .2 0 Figure 21 .1 Notation: L ,... 400 Alumina (99%) 8 25 7 1000 I500 Tungsten carbide (6% cobalt) 5 90 31 195 600 Silicon carbide (rezction bonded) 4 150 44 1100 1350 Silicon carbide (converted) 4 46 29 840 450 Carbon graphite (resin impregnated) (antimony impregnated) 5 5 18 22 13 13 75 0 75 0 25 0 400 0 .2 900 20 0 7 430 800 48 340 300 - + glass 100 Stellite (cobalt based) 12 PTFE 0.3 25 ~~ Bronze (leaded) ~ 150 17 T h e r m a l diffu:sivity... 5 d t > 2. 5 2. 0 I E 1.0 Y 1.5 w z 0 w 1.0 0 0.5 04 0.6 08 1.0 20 4.0 6.0 8 0 10.0 1I , C 05 0 1 2 3 Figure 22 .8 Calculation of mass flow rate of labyrinth B 22. 5 4 + 5 6 7 8 B 22 Labyrinths, brush seals and throttling bushes VISCOSEAL (Also called a screw seal or wind back seal) Resembles a bush seal in which a helical groove has been cut in the bore of the bush or on the shaft (Figure 22 .9) As... ‘ 0 ring; S, soft packing) B 19 .7 Selection of seals BI9 104 103 10 2 10 L m n 5 2 a 1 P a E A = 1 E 10-1 10 -2 10-3 7 bar 70 bar 7 bar ROTARY LIP SEAL OIL 0.35 bar SOFT PACKING WATER 7 bar PISTON RING OIL LABYRINTH WATER 7 bar 7 bar 10-4 Figure 19.8 Approximate leakage rates for various types of seal B 19.8 FIXED BUSHING WATER 7 bar Sealing against dirt and dust B20 When operating in dirty and dusty... 2. rra(PS - Pa) (a q m3/s or in3/s - b/ c 3 (a - 6) 4=RADIAL BUSH c3 - (Q - 24 7 a * For Mach number < 1.0, i.e fluid velocity < local velocity of sound t If shaft rotates, onset of Taylor vortices limits validity + 6 ) (P, Pa) 4=-,- 1 27 ) a 1 o g , a b < 41.3 (where v 622 .1 = kinematic viscosity) pa B 22 Labyrinths, brush seals and throttling bushes lo4; 8 7 6 5 I I INCOM PR ESSlBL E 4 3 2 p 10’ 8 7. .. extrusion 823 .4 and to provide good bearing surfaces Lir> seals 923 Extrusion clearance-mmtin) Up to 100 bar (1500 p.s.i.) - 100 -20 0 bar (150&3000 p.s.i.) Normal Normal 0 .25 (0.010) Rubber Short l i j e 0.5 (0. 020 ) - Short l$e Normal Short l$e ~~ - - 0.1 (0.005) 0 .25 (0.010) 0.1 (0.005) 0 .25 (0,010) 0.1 (0.005) 0.5 (0. 020 ) ~ Rubber/fabric leather 0.4 (0.015) 0.6 (0. 025 ) 0 .25 (0.010) 0.5 (0. 020 ) Palyurethane... foil B24.3 -60 to 100°C -50 to 140°C -50 to 100°C -45 to 110°C -30 to 120 °C -25 to 180°C - 10 to 25 0°C -100 to 25 0°C - 100 to 25 0°C 0 to 480°C B24 Mechanical seals Table 24 .5 Thermal properties of seal face materials Conductivity X 106/k Dlffusiuib W/mK Expansion coef%ient Material x lo6m2/s Maximum temperature "C continuous Specijc heat J& K Stainless steel (18/8) 16 16 4 510 600 Ni-resist 17 40 12 460... given in Figure 2 l 6 The individual diameter of the several drain holes making up the above area should not be less than 5 mm in say These are a matter of judgement Suggested values for diametral clearance are: N, rev/min 20 00 0 4000 8000 6000 2 k 1 0 20 40 60 80 100 120 N, rev15 Figure 21 .6 B21 .2 Low-speed shafts: 1 .25 X max design bearing diametra1 clearance High-speed shafts: D /25 0 or 2 X max design . 0. 025 X axial width Millimetres 25 75 3-5 3-6 76 150 5-10 5-10 15 1 -23 0 6- 12 G 12 (N.B Groove 23 0-400 10-19 10-19 tolerance H7) ~~ ~~ 400-800 12- 25 12- 25 - Inches 1-3 0. 125 -0.1 87. Inches 1-3 0. 125 -0.1 87 0. 125 -0 .21 8 3-6 0.1 87- 0. 375 0.1 874 .4 37 ~ ___~ 6-9 0 .25 0-0.500 0 .25 0-0.500 9-16 0. 375 -0 .75 0 0.3 75 -0 .75 0 16-30 0.500-1.000 0.500-1.000 Table 17. 9 Types of joints. PTFE 17 2. 26 80 GraphitelMoS2 filled PTFE 20 2. 20 115 Bronze-filled PTFE 13 3.90 I18 Resin-bonded PTFE 29 1 .75 30 Resin-bonded fabric 110 1.36 Carbon 43 1.8 43 Resin-bonded carbon 20 1.9