Mechanical engineering | Vehicles » Siegling Proposition Timing Belts, Calculation Methods

timing belts Calculation methods Contents You can find detailed information on Siegling Proposition high quality timing belts in the overview of the range (ref. no 245) Siegling – total belting solutions Formulae 2 Calculation 5 Calculation examples 7 Calculation sheets 15 Tables 26 Formulae 1. Forces Symbol Effective pull to be transmitted Designation Unit FU N Calculation/Remarks 2 · 103 · T 19.1 · 106 · P = d0 n · d0 FU = = 103 · P v [N] FU = FA + FH + FR . [N] Accelerating force FA N FA = m · a [N] Lifting power FH N FH = m · g · sin α [N] (sin α for inclined conveying) Frictional force (µ values table 4) FR N FR = m · µ · g [N] (g = 9.81 m/s2) Maximum effective pull FU max N FU max = FU · (c₂ + c₃) [N] Specific effective pull required FU req N FU req = FU max /c₁ [N] Specific effective pull FU N from calculation sheet Pretensioning force FV N FV ≥ 0.5 · FU max [N] (2-pulley drives) FV ≥ FU max [N] (linear drives) Force

determining belt selection FB N FB = FU max + FV [N] Permissible tension member load Fper N Table value from calculation sheet External force F N Static shaft load FWS N FWS = 2 · FV [N] (2-pulley drives) 2. Masses Symbol Designation Unit Calculation/Remarks Mass to be moved Mass of belt Belt weight per metre m mR mR kg kg kg/m m = mR + mL + mZ red + mS red [kg] mR = mR · l/1000 [kg]; Table value from calculation sheet Mass of linear slide mL kg Mass of timing belt pulley mZ kg mZ = mZ red kg mZred = mS kg mS = mS red kg mSred = Reduced mass of timing belt pulley Mass of take-up pulley Reduced mass of take-up pulley (dk2 - d2) · π · b · ρ [kg] 4 · 106 mZ d2 · 1+ 2 dk 2 [kg] (dS2 - d2) · π · b · ρ [kg] 4 · 106 mS d2 · 1+ 2 dS 2 [kg] 2 3. Measurements Symbol Designation Unit Calculation/Remarks Bore diameter d mm Pitch diameter d0 mm d0 = z · t/π [mm], catalogue value Outside diameter dk mm Catalogue value of timing belt pulley

supplier Take-up pulley diameter ds mm Width of timing belt pulley, take-up pulley b mm Belt width b₀ mm Belt length untensioned l mm for i = 1: for 2-shaft drives l = 2 · e + π · d₀ = 2 · e + z · t [mm] for i ≠ 1: l= Belt length general mm Clamping length per belt end lk mm Centre distance (exact) e mm Centre distance (exact) Δe mm FV · l 2 · cspec FV · l 2 · cspec [mm] ∆e ∆e [mm] ∆e e e Clamped belt (AdV 07) e ∆e = 2 l = z · t [mm] for AdV 07 is calculated from l Rotating 2-pulley drives and 2-pulley linear drives (AdV 07clamped): ∆e = ∆e = t · (z2 + z1) 1 t · (z2 – z1) + 2e + 2 4e π FV · l [mm] cspec ∆e e F ·l ∆e = V [mm] c spec Positioning deviation under influence of external forces Δs mm c Belt pitch t mm Centre distance of adjacent teeth Calculation/Remarks ∆s = F [mm]; ∆smin = F [mm] cmax 4. Constants and Coefficients Symbol Designation Unit Density ρ kg/dm3 e.g pulley

material Friction coefficient μ Teeth in mesh factor; c1 number of teeth involved in power flux Depends on friction pairing; see table 4 i = 1; c1 = z/2 Operational factor c2 Acceleration factor c3 Note c1 max table 1! Table 2 Table 3 3 i ≠ 1; c1 = z1 (z – z ) · t · arc cos 2 1 180 2·π·e Formulae 5. Quantities of Motion Symbol Designation Unit Calculation/Remarks Speed (RPM) n min-1 n= v · 19,1 · 103 [min-1] d0 Belt speed v m/s v= d0 · n = 19.1 · 103 Acceleration a m/s2 Acceleration due to gravity Travel total g sv m/s2 mm g = 9.81 [m/s2] sv = sa + sa + sc [mm] Accelerating (braking) distance Travel where v = constant sa (sa) sc mm mm sa (sa) = Accelerating (braking) time ta (ta) s ta (ta) = 2 · sa · a 1000 [m/s] a · ta2 · 103 v2 · 103 = [mm] 2 2·a sc = v · tc · 103 [mm] v = a 2 · sa a · 1000 Travel time where v = constant tc s sc tc = [s] v · 103 Travel time total Gear ratio tv i s tv = ta

+ ta + tc [s] [s] 6. Other Values/Abbreviations Symbol Angle of incline Specific spring rate Spring rate of a belt Spring rate of a linear drive Designation Unit Calculation/Remarks α ° for inclined conveying cspec N Table value from calculation sheet c N/mm generally: c = l c= l ·l l1 1 m2L Determine from extreme positions of linear drive cmin/cmax l = l1 + l2 [mm] l2 l = l1 + l2 [mm] l2 l cmin1= cmin for l₁ = l₂ Natural frequency fe Exciter frequency f0 Power to be transmitted · cspec [N/mm] mL l1 N/mm l1 Tooth base service factor Tension member service factor Number of teeth Number of teeth on small pulley Number of teeth on large pulley Minimum number of teeth Minimum take-up pulley diameter cspec [N/mm] l l2 4 · cl2 spec 4·cl [N/mm] spec cmin = [N/mm] l 1 c · 1000 fe = [s-1] · s-1 2π mL n s-1 f0 = [s-1] 60 Stooth Stooth = FU/FU req Stm Stm = Fper/FB z where i = 1 z1 where i ≠ 1 z2 where i ≠ 1 zmin Table value

from calculation sheet ds min mm Table value from calculation sheet P kW P= FU · n · d0 F ·v = U 3 [kW] 10 19.1 · 106 Torque to be transmitted T Nm T = FU · d0 [Nm] 2 · 103 Timing belt open AdV 07 Timing belt welded endless AdV 09 4 Calculation method for B 92 timing belts FU = 2 · 103 · T 19.1 · 106 · P 103 · P = = d0 n · d0 v and v= d0 · n [m/s] 19.1 · 103 with d0 = [N] z·t π Effective pull FU [N] to be transmitted 1 Maximum effective pull FU max [N] 2 Teeth in mesh factor c1 for the driving (smaller) pulley 3 Specific effective pull required FU req [N] 4 [mm] or: Sum of all forces FU = FR + FH + FA [N] FR = m · µ · g [N] frictional force in which: FH = m · g or m · g · sin α [N] lifting power FA = m · a [N] accelerating force Operational and acceleration factor c2 and c3 take from tables 2 and 3 FU max = FU · (c2 + c3) [N] c1 = z/2 for i = 1 z (z – z ) · t c1 = 1 · arc cos 2 1 180 2·π·e for i ≠ 1 Always

round down calculated values for c1 to the smaller round figure. Note maximum values in table 1! Estimate number of teeth if not given and determine n. FU req = FU max c1 [N] Find FU req in the belt overview graph and move horizontally to the right to the point of intersection with the speed in question. All belt pitches which lie above this point can be used in principle. Select belt type and find point of intersection on the calculation sheet for that particular type. The curve above the point of intersection gives the belt width b0 [mm] The point where speed and width curve intersect gives the transmittable effective pull FU [N]. l = 2 · e + z · t = 2 · e + π · d0 [mm] for i = 1 2 t · (z2 – z1) 1 t · (z2 – z1) for i ≠ 1 l= [mm] + 2e + π 2 4e I must always be an integral multiple of the belt pitch t in mm. Equations are valid for rotating 2-pulley drives. Calculate other designs according to their geometry. mR = mR · l/1000 [kg]; mR from calculation

sheet For calculation see formulae. Timing belt pulley measurements from catalogue. 5 Belt selection from graphs FU [N] of selected belt type Belt length l [mm] Belt mass mR [kg] Reduced mass of timing belt pulley and take-up pulleys mZ red, mS red [kg]. 5 Calculation method for B 92 timing belts 6 Check FU with FA including mR , mZ red and mS red 7 Determining tooth base 8 Pretensioning force [N] Force determining belt selection FB [N] Determining tension member service factor Stm 9 Repeat steps 1 – 4 if the influence of the belt mass must not be neglected; e.g on linear drives with high acceleration FU · c1 FU max Stooth = = FU FU req Demand: Stooth > 1 FV > 0.5 · FU max [N] FV > FU max [N] for 2-pulley drives for linear drives FB = FU max + FV [N] Stm = Demand: stm > 1 Fper from calculation sheet Fper FB Take-up range Δe [mm] Rotating 2-pulley drives and 2-pulley linear drive (AdV 07 clamped) (For endless belts: Elongation at

fitting ε approx. 01 % For open material: Elongation at fitting ε approx. 02 %) FV · l ∆e = 2 · cspec ∆e [mm] e Clamped belt (AdV 07) ∆e F ·l ∆e = V [mm] cspec e Steps 10 – 12 of calculation method only for linear drives as a rule! 10 Spring rate of entire system c [N/mm] and cmin [N/mm] l · cspec [N/mm]; l = l1 + l2 l1 · l2 c= l1 l2 cmin and cmax as per extreme right and left positions of slide. cmin = 11 12 Positioning deviation under influence of external force Δs [mm] Resonance behaviour: Natural frequency: fe [s-1] Exciter frequency: f0 [s-1] ∆s = 4 · cspec l [N/mm] for l1 = l2 F [mm] c ∆smax = F [mm] cmin 1 · 2π c · 1000 m fe = l1 l2 ∆s F [s-1] fe ≠ f 0 There is then no danger of resonance. n f0 = [s-1] 60 6 Calculation example 1 Linear drive for moving assembly carriers Travel Speed Acceleration Mass of slide Frictional force of guide rails Slide length d0 SV = 2500 mm v = 3 m/s = const.; i = 1 a = 15 m/s2 mL

= 25 kg incl. assembly carrier + goods being carried FR = 80 N lL = 400 mm approx. 100 mm Diagram 50 400 2500 50 Required: Belt type and width b0, RPM, timing belt pulley data, pretensioning force and take-up range, effective pull, positioning accuracy FU = FA + FR [N] FA = 25 kg · 15 m/s2 = 375 N FU = 375 N + 80 N = 455 N Mass of timing belt pulley and belt neglected. Effective pull FU [N] Effective pull FU [N] to be transmitted – approximate. Operational and acceleration c2 and c3 c2 = 1.4 because of high acceleration c3 = 0 as i = 1 455 N · 1.4 = FU max = 637 N Selected: c1 = 12 for open material Zmin = 24; Where d0 ≈ 100 mm and c1 = 12 i.e 14 und 20 mm pitches ruled out due to d0! FU req = n= 7 FU max = 53.08 N c1 v · 19.1 · 103 d0 = 573 min-1 1 2 FU max – approximate. Teeth in mesh factor c1 3 FU req 4 n from given values d0 and v Calculation example 1 Linear drive for moving assembly carriers 1500 AT 20/100 mm For linear drives

preferably use AT and HTD! Possible types: AT 5, AT 10, HTD 8M. FU [N] Belt selection 1200 HTD 14M/115 mm 1100 1000 T 20/100 mm 900 800 AT 10/100 mm 700 600 HTD 8M/85 mm 500 T 10/8mm H/101,6 mm 400 L/101,6 mm 300 200 AT 5/50 mm T 5/50 mm 100 10 100 1000 [1/min] 10000 Overview graph 800 Selected: AT 10 because of high spring resistance; t = 10 mm. FU [N] FU of selected belt type AT10 100 600 75 500 400 50 300 32 200 FU 140 N FU req 53 N FU = 140 N 25 100 0 10 100 1000 [1/min] 10000 572 AT 10 graph 5 Selecting timing belt pulley d0 = 100 mm => 100 · π = 314 / t = 31.4 teeth Selected: Z = 32; standard pulley Material aluminium; ρ = 2.7 kg/dm3 d0 = 32 · t/π = 101.86 mm therefore: v · 19.1 · 103 n= Mass of timing belt pulley Calculate belt length = 562 min-1 dK = 100 mm; d = 24 mm; b = 32 mm ⇒ mZ = Reduced mass of timing belt pulley 101.86 (1002 - 242) · π · 32 · 2.7 = 0.64 kg 4 · 106 mZ red = 0.64 242 · 1+ 2 1002 =

0.34 kg l = 2 · (2500 + 400 + 100 + d0) - (400 - 2 · 80) + z · t l = 6283.7 mm => l = 6290 mm from diagram and d0 ; clamping length lK per belt end = 80 mm. Determining belt mass mR = 0.064 kg/m · 25 cm = 016 kg/m mR = 1.00 kg 8 FA = (25 kg + 1 kg + 2 · 0.34 kg) · a FA = 400.2 N FU = 400.2 + 80 = 480 N FU max = 480 · 1.4 = 675 N FU req = 56.02 N FU FUreq Stooth = = 140 = 2.5 56.02 >1 Fper 3750 Demand fulfilled S = = 2.24 >1 tm = 1675 FV · l 2 · cspec = cmin = l 6290 - 2 · 80 · cspec= · cspec = 662.77 N/mm l1 · l2 2684 · 3446 cmax = l 6290 - 2 · 80 · cspec = · cspec = 5602.96 N/mm l1 · l2 184 · 5946 External force here: FR = 80 N ∆smin = FR = 0.014 mm cmax ∆smax = FR = 0.122 mm cmin 1 · 2π cmin · 1000 mL f0 = n 562 = = 9,4 s-1 60 60 = 25.7 s-1 i.e no danger of resonance Timing belt 25 AT 10, 6290 mm long Timing belt pulley with Z = 32 für 25 mm belt Take-up range to generate FV Δe = 3.14 mm n = 562 min-1

Δsmax = 0.122 mm 9 7 Force determining belt selection FB 8 Tension member service factor Stm Fper from calculation sheet for AT 10 1000 N · 6290 mm = 3.14 mm 2 · 106 N fe = Tooth base service factor Stooth Pretensioning force FV FB = FV + FU max = 1675 N ∆e = 6 Demand fulfilled FV ≥ FU max for linear drives! FV selected = 1.5 FU max = 1000 N FB FU max exact including mR and mZ red Take-up range Δe [mm] cspec from calculation sheet for AT 10 Spring rate of system cmin; cmax 9 10 l1 and l2 from diagram! Positioning accuracy due to external force 11 Natural frequency of system 12 Exciter frequency Result If Δsmax has to be smaller, b0 = 32 mm would be selected. No danger of resonance. Calculation example 2 Drag band conveyor for workpiece tray Diagram d0 ≤ 80 mm 20 000 Speed Mass of tray incl. load Maximum loading Belt support tight side Belt support slack side Centre distance Start Operation Pulley diameter v = 0.5

m/s m = 1.8 kg 20 trays Plastic rails Rollers e = 20000 mm Without load continuous operation, purely conveying d0 ≤ 80 mm Required: Belt type, length, take-up range, timing belt pulley data 1 Effective pull FU [N] Effective pull FU [N] to be transmitted without belt mass. FU here = FR, as acceleration negligible. FU = FR = m · µ · g µ selected approx. 025 from table 4 m = 20 · 1.8 kg = 36 kg FU = FR = 36 · 9.81 · 025 = 883 N 2 Operational and acceleration factor c3 = 0, as i = 1 c2 = 1.2 selected (20 % reserve) FU max = 1.2 · 83 N = 106 N for 2 belts FU max = 53 N per belt 3 Teeth in mesh factor c1 selected = c1 max = 6 for AdV 09 Belt rotates and has been welded endless. 4 Specific effective pull required FU req FU req = Speed FU max = 8.8 N c1 1500 FU [N] AT 20/100 mm 1200 v · 19.1 · 103 n= 75 HTD 14M/115 mm 1100 where d0 = 75 mm 1000 T 20/100 mm 900 800 = 127 min-1 AT 10/100 mm 700 600 HTD 8M/85 mm 500 T 10/8mm H/101,6 mm 400 L/101,6 mm

300 The narrowest belt is already sufficient. Selected: 2 pieces 16 T 5. 16 mm width to provide greater support for tray. AT 5/50 mm T 5/50 mm 100 10 100 1000 [1/min] 10000 Overview graph 120 50 T5 FU [N] Belt selection 200 100 90 80 32 70 60 FU [N] of selected belt type 25 50 FU = 34 N FU 34 N 40 16 30 10 20 FU req 8.8 N 10 0 10 100 127 1000 [1/min] 10000 T 5 graph 10 d0 · π teeth = Z = 47.1 Selecting timing belt pulley t 5 Selected: Z = 48 teeth; standard pulley l = Z · t + 2 · e = 40240 mm Belt length mR = l · mR = 0.038 kg/m · 4024 m = 153 kg Belt mass FU max = FR · 1.2 FR = (20 · 1.8 kg + 2 · 153 kg) · 981 · 025 = 958 N FU max = 115 N = 57.5 N/belt If increase is negligible, further calculation unnecessary FU max including mR of tight side 6 Tooth base service factor 7 Pretensioning force FV 8 Stooth = FU · c1 FU max = 34 · 6 = 3.69 57.5 >1 Demand fulfilled FV ≥ 0.5 · FU max Selected: FV = 40 N FB = FV +

FU max = 40 + 57.5 = 975 N Force determining belt selection FB Fper 270 N Demand fulfilled S = = 2.8 >1 tm = FB 97.5 N Fper from calculation sheet for 16 T5 Adv 09 Tension member service factor Stm Take-up range Δe ∆e = FV · l 2 · cspec ∆e = 40 · 40240 = 6.7 mm 2 · 0.12 · 106 with cspec = 0.12 · 106 from calculation sheet 2 pieces timing belt type 16 T 5, 40240 mm long, AdV 09 Timing belt pulley with Z = 48 teeth for 16 mm belt Take-up range to generate FV Δe = 6.7 mm 11 Result 9 Calculation example 3 Lifting device Diagram Travel Speed Medium acceleration/deceleration 3500 500 2500 Max. deceleration (emergency shutdown) Slide mass with load No. of belts Frictional force of guide rails d0 2500 mm 2 m/s 4 m/s2 10 m/s2 75 kg 2 pieces FR = 120 N maximum 150 mm Required: Belt type and length, pretensioning force, take-up range, speed. Rough operating conditions! 1 Effective pull FU [N] Effective pull FU [N] to be transmitted. FU = FA + FH +

FR + FR = 120 N FA = 75 kg · 4 m/s2 = 300 N FA max = 75 kg · 10 m/s2 = 750 N (emergency shutdown) FH = 75 kg · 9.81 m/s2 = 736 N FU = 120 N + 736 N + 750 N (emergency braking during descent) FU = 1606 N 2 Operational factor c2 Acceleration factor c3 c3 = 0 as i = 1 c2 = 2.0 because of rough operating conditions FU max = 1606 · 2 = 3212 N distributed between 2 belts FU max= 1606 N pro belt 3 Teeth in mesh factor c1 Open material: c1 = 12 = c1 max for AdV 07 selected => Zmin = 24; t = 20 ruled out because of d0 max 4 Specific effective pull required FU req FU max = 133 N 12 1500 AT 20/100 mm per belt! FU [N] FU req = 1200 HTD 14M/115 mm 1100 1000 Speed Where d0 = 140 mm T 20/100 mm 900 800 AT 10/100 mm 700 v · 19.1 · 103 n= d0 = 273 min-1 600 HTD 8M/85 mm 500 T 10/8mm H/101,6 mm 400 L/101,6 mm 300 200 All types between L and HTD 14M are possible. Selected: HTD 14M because of large reserves. Designation: 40 HTD 14M AT 5/50 mm T 5/50 mm 100 10

100 1000 [1/min] 10000 Overview graph 1300 FU [N] Belt selection HTD 14M 115 1100 1000 900 85 800 700 FU [N] of selected belt type FU = 306 N 600 55 500 40 400 FU 306 N FU req 133 N 300 200 100 10 100 1000 273 [1/min] 10000 12 HTD 14M graph Z= d0 · π = t 140 · π = 31.4 14 Pulley selected => n = 268 min-1 Selected: Z = 32; standard pulley l = 3500 · 2 + Z · t – 500 + 2 · 114 l = 7176 mm 512.6 teeth l selected: 512 teeth 7168 mm Belt length mR · l = 0.44 kg/m · 7168 m = 3155 kg/belt Belt mass mZ = 6.17 kg dK = 139.9 mm d = 24.0 mm Timing belt pulley data mZ red = mZ 2 (catalogue values) (catalogue values) (catalogue values) · 1+ 5 d2 = 3.18 kg dK2 Reduced mass of timing belt pulley gives in total: 4 · 3.18 = 127 kg FU = FA + FH + FR FH = 736 N FR = 120 N FA = (75 kg + 12.7 kg + 2 · 3155 kg) · 10 m/s2 = 940 N FU with belt and pulley mass considered 6 Tooth base service factor Stooth 7 FU = 940 + 120 + 736 = 1800 N FU

max = c2 · FU = 3600 N; distributed between 2 belts => FU max = 1800 N/belt FU req = Stooth = 13 1800 = 150 N 12 FU 310 = = 2.07 FU req 150 >1 Demand fulfilled Calculation example 3 Lifting device 8 9 Selecting pretensioning force FV ≥ FU max = 1800 Selected: 2000 N = FV Force determining belt selection FB FB = FU max + FV = 3800 N Permissible force on each strand Fper = 8500 N Tension member service factor Stm Fper 8500 S = = 2.24 >1 Demand fulfilled tm = FB 3800 Take-up range Δe cspec = 2.12 · 106 N ∆e = FV · l 2 · cspec = 7168 · 2000 = 3.38 mm 2 · 2.12 · 106 Result Timing belt type 40 HTD 14M 7168 mm long = 512 teeth Timing belt pulleys à 32 teeth for 40 mm wide belt Take-up range to generate force FV Δe = 3.38 mm Safety note In the case of lifting devices the regulations of professional/trade associations should be observed. If necessary, safety from breakage must be proven from the breaking load of the belt. With open

material AdV 07 this is approximately 4 times the permissible force on each strand Fper. Exact values on request. 14 Overview graph 1500 FU [N] AT 20/100 mm 1200 HTD 14M/115 mm 1100 1000 T 20/100 mm 900 800 AT 10/100 mm 700 600 HTD 8M/85 mm 500 T 10/100mm H/101.6 mm 400 L/101.6 mm 300 200 AT 5/50 mm T 5/50 mm 100 0 10 15 100 1000 [1/min] 10000 Calculation sheet Timing belt type T 5 120 50 FU [N] Specific effective pull T5 100 90 80 32 70 60 25 50 40 16 30 10 20 10 0 10 100 1000 [1/min] 10000 Characteristic values: Type T 5 (steel tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 10 150 310 0.08 0.024 16 230 460 0.12 0.038 25 410 830 0.19 0.06 32 460 930 0.24 0.077 50 830 1660 0.38 0.12 32 600 1200 0.18 0.064 50 900 1800 0.29 0.10 Characteristic values: Type T 5 (Kevlar tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 10 210 430

0.06 0.020 16 300 610 0.09 0.032 25 490 980 0.14 0.050 * The specifications stated are empirical. Nevertheless, our specifications do not cover all applications on the market It is the OEM’s responsibility to check whether Forbo Siegling products are suitable for particular applications. The data provided is based on our in-house experience and does not necessarily correspond to product behaviour in industrial applications. Forbo Siegling cannot assume any liability for the suitability and reliability in different processes of its products Furthermore, we accept no liability for the results produced in processes, damage or consequential damage in conjunction with the usage of our products. 16 Calculation sheet Timing belt type AT 5 180 50 FU [N] Specific effective pull AT 5 140 120 32 100 25 80 60 16 40 10 20 0 10 100 1000 [1/min] 10000 Characteristic values: Type AT 5 (steel tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106

mR [kg/m] 10 320 640 0.17 0.03 16 560 1120 0.27 0.048 25 920 1840 0.42 0.075 32 1120 2240 0.54 0.096 50 1840 3680 0.84 0.15 32 1172 1562 0.41 0.086 50 1851 2468 0.63 0.135 Characteristic values: Type AT 5 (Kevlar tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 m‘R [kg/m] 10 341 455 0.13 0.027 16 568 757 0.20 0.043 25 908 1210 0.32 0.068 * See comment on page 16 17 Calculation sheet Timing belt type T 10 500 FU [N] 100 Specific effective pull T 10 400 75 350 300 250 50 200 32 150 25 100 16 50 0 10 100 1000 [1/min] 10000 Characteristic values: Type T 10 (steel tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 16 650 1300 0.32 0.077 25 1100 2200 0.5 0.12 32 1300 2600 0.64 0.154 50 2200 4400 1.0 0.24 75 3300 6600 1.5 0.36 100 4400 8800 2.0 0.48 50 1980 3970 0.75 0.20 75 2450 4900 1.13 0.30 100 3350 6700 1.5 0.40 Characteristic values: Type T 10

(Kevlar tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 16 500 1000 0.24 0.064 25 870 1750 0.38 0.10 32 1170 2350 0.48 0.128 * See comment on page 16 18 Calculation sheet Timing belt type AT 10 FU [N] 800 Specific effective pull 100 AT 10 600 75 500 400 50 300 32 200 25 100 0 10 100 1000 [1/min] 10000 Characteristic values: Type AT 10 (steel tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 25 1920 3840 1.0 0.16 32 2280 4560 1.28 0.205 50 3840 7680 2.0 0.32 75 5760 11520 3.0 0.48 100 7680 15360 4.0 0.64 75 4113 5483 2.25 0.315 100 5513 7350 3.0 0.420 Characteristic values: Type AT 10 (Kevlar tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 25 1313 1750 0.75 0.105 32 1705 2273 0.96 0.134 50 2713 3617 1.5 0.210 * See comment on page 16 19 Calculation sheet Timing belt type T 20 1000 FU [N] 100

Specific effective pull T 20 800 75 700 600 500 50 400 32 300 25 200 100 0 10 100 1000 [1/min] 10000 Characteristic values: Type T 20 (steel tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 25 1680 3360 0.88 0.193 32 2160 4320 1.32 0.246 50 3360 6720 1.75 0.385 75 5040 10080 2.63 0.578 100 6720 13440 3.5 0.77 75 4200 8400 1.97 0.48 100 5500 11000 2.63 0.64 Characteristic values: Type T 20 (Kevlar tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 25 1450 2900 0.66 0.16 32 1870 3750 0.99 0.205 50 2850 5700 1.31 0.32 * See comment on page 16 20 Calculation sheet Timing belt type AT 20 FU [N] 1600 Specific effective pull 100 AT 20 1200 75 1000 800 50 600 32 400 25 200 0 10 100 1000 [1/min] 10000 Characteristic values: Type AT 20 (steel tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 25 3300

6600 1.56 0.25 32 4400 8800 2.00 0.32 50 6600 13200 3.13 0.50 75 9900 19800 4.69 0.75 100 13200 26400 6.25 1.0 75 4125 5500 3.52 0.548 100 5531 7375 4.69 0.730 Characteristic values: Type AT 20 (Kevlar tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 25 1313 1750 1.17 0.183 32 1706 2275 1.5 0.234 50 2719 3625 2.35 0.365 * See comment on page 16 21 Calculation sheet Timing belt type L = 3/8 t = 9.525 mm FU [N] 400 101,6 Specific effective pull L 300 76,2 250 200 50,8 150 38,1 100 25,4 19,1 50 12,7 0 10 100 1000 [1/min] 10000 Characteristic values: Type L = 3/8" (steel tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 12.7 550 1100 0.25 0.05 19.1 800 1600 0.38 0.074 25.4 1100 2200 0.5 0.099 38.1 1600 3200 0.75 0.149 50.8 2200 4400 1.0 0.198 76.2 3300 6600 1.5 0.297 101.6 4400 8800 2.0 0.396 50.8 1660 3320 0.75 0.163 76.2 2480 4960 1.13

0.244 101.6 3320 6640 1.5 0.325 Characteristic values: Type L = 3/8" (Kevlar tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 12.7 410 830 0.19 0.041 19.1 620 1250 0.29 0.061 25.4 830 1600 0.38 0.081 38.1 1240 2480 0.56 0.122 * See comment on page 16 22 Calculation sheet Timing belt type H = 1/2 t = 12.7 mm 450 FU [N] 101,6 Specific effective pull H 350 76,2 300 250 50,8 200 38,1 150 25,4 100 19,1 12,7 50 0 10 100 1000 [1/min] 10000 Characteristic values: Type H = 1/2" (steel tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 12.7 500 1000 0.25 0.057 19.1 800 1600 0.38 0.086 25.4 1100 2200 0.5 0.114 38.1 1600 3200 0.75 0.171 50.8 2200 4400 1.0 0.229 76.2 3300 6600 1.5 0.343 101.6 4400 8800 2.0 0.457 50.8 1660 3320 0.75 0.178 76.2 2450 4900 1.13 0.267 101.6 3150 6300 1.5 0.356 Characteristic values: Type H = 1/2" (Kevlar tension

member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 12.7 410 830 0.19 0.044 19.1 620 1250 0.29 0.067 25.4 830 1660 0.38 0.089 38.1 1240 2480 0.56 0.133 * See comment on page 16 23 Calculation sheet Timing belt type HTD 8M FU [N] 600 Specific effective pull 85 HTD 8M 500 450 400 350 50 300 250 200 30 150 20 100 50 0 10 100 1000 [1/min] 10000 Characteristic values: Type HTD 8M (steel tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 20 1440 2880 0.7 0.138 30 2400 4800 1.05 0.207 50 3840 7680 1.75 0.345 85 7320 14640 2.98 0.587 Characteristic values: Type HTD 8M (Kevlar tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 20 1033 1377 0.53 0.094 30 1593 2123 0.79 0.142 50 2713 3617 1.31 0.236 85 4673 6230 2.24 0.400 * See comment on page 16 24 Calculation sheet Timing belt type HTD 14M FU [N] 1300 115 Specific

effective pull HTD 14M 1100 1000 900 85 800 700 600 55 500 40 400 300 200 100 0 10 100 1000 [1/min] 10000 Characteristic values: Type HTD 14M (steel tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 40 5500 11000 2.12 0.44 55 7970 15950 2.92 0.605 85 12650 25300 4.51 0.935 115 17600 35200 5.83 1.265 Characteristic values: Type HTD 14M (Kevlar tension member)* Value b0 [mm] Fper [N] AdV 09 Fper [N] AdV 07 Cspec [N] · 106 mR [kg/m] 40 1874 2499 1.59 0.336 55 2612 3482 2.19 0.462 85 4087 5449 3.38 0.714 115 5562 7416 4.37 0.966 * See comment on page 16 25 Tables Table 1 Teeth in mesh factor c1 Application c1 max Welded belts AdV 09 Open belts AdV 07 Linear drives with higher positioning accuracy 6 12 4 c1 = Number of teeth involved in power flux Table 2 Operational factor c2 Table 3 Acceleration factor c3 Table 4 Friction coefficients of timing belts Smooth operating conditions c2 = 1.0

Short-term overload < 35 % Short-term overload < 70 % Short-term overload < 100 % c2 = 1.10 – 135 c2 = 1.40 – 170 c2 = 1.75 – 200 Transmission ratio i i > 1 to 1.5 i > 1.5 to 25 i > 2.5 to 35 i > 3.5 µ c3 0.1 0.2 0.3 0.4 PU Bed/rail 0.5 Plastic support rail 0.2 – 03 Accumulation 0.5 PAZ 0.2 – 03 0.2 – 025 0.2 – 03 PAR 0.2 – 03 0.2 – 025 0.2 – 03 All values are guidelines PU = polyurethane PAZ = polyamide fabric on toothed side PAR = polyamide fabric on back of belt 26 Resistances Chemical Acetic acid 20 % Resistance ❍ Acetone ❍ Aluminium chloride, aqueous 5 % Ammonia 10 % Aniline – ASTM oil 1 ASTM oil 2 Resistance Lubricating grease (sodium soap fat) Methyl alcohol ❍ Methyl alcohol/Benzine 15-85 Methyl ethyl ketone ❍ Methylene chloride – Mineral oil n-Heptane n-Methyl-2-pyrrolidone – Nitric acid 20 % – Petrol, regular Petrol, super Potash lye 1 N ❍ Sea

water Soda lye 1 N ❍ Sodium chloride solution, conc. Sodium soap fat Sodium soap fat + 20 % water ❍ Sulphuric acid 20% ❍ Tetrahydrofurane – Toluene – Trichloroethylene – Water ASTM oil 3 ❍ Benzol ❍ Butyl acetate – Butyl alcohol ❍ Carbon tetrachloride – Common salt solution, conc. Cyclohexanol ❍ Diesel oil Dimethyl formamide – Ethyl acetate – Ethyl alcohol ❍ Ethyl ether Hydrochloric acid 20 % ❍ Iron chloride, aqueous 5 % ❍ Isopropyl alcohol ❍ Kerosine 27 Chemical Table 5 Chemical resistance at room temperature Symbols = good resistance ❍ = limited resistance; slight weight and dimensional changes­ after a certain period of time – = no resistance Metrik GmbH · Werbeagentur · Hannover · www.metriknet Technologiemarketing · Corporate Design · Technical Content Siegling – total belting solutions Forbo Siegling service – anytime, anywhere

Ref. no 202-2 The Forbo Siegling Group employs more than 2,000 people. Our products are manufactured in nine production facilities across the world. You can find companies and agencies with warehouses and workshops in over 80 countries. Forbo Siegling service points are located in more than 300 places worldwide. Forbo Siegling GmbH Lilienthalstrasse 6/8, D-30179 Hannover Phone +49 511 6704 0, Fax +49 511 6704 305 www.forbo-sieglingcom, siegling@forbocom Forbo Movement Systems is part of the Forbo Group, a global leader in flooring, bonding and movement systems. www.forbocom 07/13 · UD · Reproduction of text or parts thereof only with our approval. Subject of change Because our products are used in so many applications and because of the individual factors involved, our operating instructions, details and information on the suitability and use of the products are only general guidelines and do not absolve the ordering party from carrying out checks and tests themselves. When we

provide technical support on the application, the ordering party bears the risk of the machinery functioning properly