Mercedes-Benz 4G-Tronic transmission

Mercedes-Benz 4G-Tronic transmission is the unofficial name given to the transmission by car enthusiasts. It was produced from 1979 to 1996 in W4A 040, W4A 028 (both type 722.3), W4A 020 (type 722.4), and W5A 030 (type 722.5) variants.

The W4A 040 and the W4A 020 were used until mid-1996. The W4A 028 variant was used for off-road applications (RWD and 4X4). The W5A 030 is basically the same transmission with an additional electrically controlled 5th gear overdrive section attached to the main body in a separate housing; it was available as an extra charge option. All 4G-Tronics were succeeded by the more modern and economic 5G-Tronic (Type 722.6) transmission that features an integrated 5th gear overdrive ratio, torque converter lock-up and fully electronic control.

The 4G-Tronic transmission is a hydraulically operated 4-speed automatic without lock-up that replaced the similarly designed W3A 040, W3B 050, and W4B 025 family of automatic transmissions with the introduction of the W126 S-Class in 1979. In some models it is calibrated to move off in second gear to reduce "creeping" and provide a smoother ride, selecting 1st only if the selector is in "2" or in case of abrupt acceleration. Other calibrations have the transmission rest in 2nd gear and kick down to 1st as soon as the accelerator is touched but before the throttle is opened. In some V8 installations a small control unit activates the kick down solenoid when the brake pedal is released so that the car moves off in 1st gear. Other attributes of this transmission include a 2-3 shift delay when the engine is cold in order to speed up catalyst warm-up. 4th gear is a 1:1 ratio. Controls are all mechanical and pneumatic, except for the kickdown solenoid and 2-3 upshift delay solenoid on some models.

In some markets a W-S (Winter - Standard / Sport) switch was provided on the shifter. Activating S mode changes a linkage which effectively shortens the throttle pressure bowden cable. This causes later, higher RPM shifts and on some models a move off in 1st gear instead of 2nd. On V8 models a B (Brake) range is available on the shifter. This activates the kickdown solenoid, forcing the transmission to shift down to 1st sooner for increased engine braking. A hydraulically activated piston prevents shifting into Reverse when the car is moving forward.

Models from 1990 and earlier allow for push starting the engine. They are fitted with a secondary fluid pump, driven by the transmission output shaft. When the vehicle is rolling at 20 mph shifting from Neutral to the 2 range will couple power to the engine. The secondary pump and thus the push starting facility was eliminated for the 1991 model year.

It is considered by enthusiasts to be one of the most reliable transmissions ever built by Mercedes-Benz with some examples exceeding 300,000 miles of service.

"To simplify production, the front group is now formed by a Ravigneaux set, which is immediately followed by the second group. This largely eliminates the need for hollow shafts and other connecting bells, which are so commonly found in planetary gearboxes. Where possible, sheet metal or die-cast parts are used. Cost-intensive material machining is limited to the manufacture of gears, shafts, and bolts."^[1]

Gearset Concept: Cost-Effectiveness^[a]

With Assessment	Output: Gear Ratios	Innovation Elasticity[b] Δ Output : Δ Input	Input: Main Components
			Total	Gearsets	Brakes	Clutches
W4A Ref. Object	${\displaystyle n_{O1}}$ ${\displaystyle n_{O2}}$	Topic[b]	${\displaystyle n_{I}=n_{G}+}$ ${\displaystyle n_{B}+n_{C}}$	${\displaystyle n_{G1}}$ ${\displaystyle n_{G2}}$	${\displaystyle n_{B1}}$ ${\displaystyle n_{B2}}$	${\displaystyle n_{C1}}$ ${\displaystyle n_{C2}}$
Δ Number	${\displaystyle n_{O1}-n_{O2}}$		${\displaystyle n_{I1}-n_{I2}}$	${\displaystyle n_{G1}-n_{G2}}$	${\displaystyle n_{B1}-n_{B2}}$	${\displaystyle n_{C1}-n_{C2}}$
Relative Δ	Δ Output ${\displaystyle {\tfrac {n_{O1}-n_{O2}}{n_{O2}}}}$	${\displaystyle {\tfrac {n_{O1}-n_{O2}}{n_{O2}}}:{\tfrac {n_{I1}-n_{I2}}{n_{I2}}}}$ ${\displaystyle ={\tfrac {n_{O1}-n_{O2}}{n_{O2}}}\cdot {\tfrac {n_{I2}}{n_{I1}-n_{I2}}}}$	Δ Input ${\displaystyle {\tfrac {n_{I1}-n_{I2}}{n_{I2}}}}$	${\displaystyle {\tfrac {n_{G1}-n_{G2}}{n_{G2}}}}$	${\displaystyle {\tfrac {n_{B1}-n_{B2}}{n_{B2}}}}$	${\displaystyle {\tfrac {n_{C1}-n_{C2}}{n_{C2}}}}$
W4A W4B 025[c]	4[d] 4[d]	Progress[b]	8 8	3[e] 3	3 3	2 2
Δ Number	0		0	0	0	0
Relative Δ	0.000 ${\displaystyle {\tfrac {0}{4}}}$	0.000[b] ${\displaystyle {\tfrac {0}{4}}:{\tfrac {0}{8}}={\tfrac {0}{4}}\cdot {\tfrac {8}{0}}={\tfrac {0}{4}}}$	0.000 ${\displaystyle {\tfrac {0}{8}}}$	0.000 ${\displaystyle {\tfrac {0}{3}}}$	0.000 ${\displaystyle {\tfrac {0}{3}}}$	0.000 ${\displaystyle {\tfrac {0}{2}}}$
W4A ZF 4HP 22	4[d] 4[d]	Early Market Position[b]	8 10	3[e] 3	3 4	2 3
Δ Number	0		-2	0	-1	-1
Relative Δ	0.000 ${\displaystyle {\tfrac {0}{4}}}$	0.000[b] ${\displaystyle {\tfrac {0}{4}}:{\tfrac {-2}{10}}={\tfrac {0}{4}}\cdot {\tfrac {10}{-2}}={\tfrac {0}{-8}}}$	−0.200 ${\displaystyle {\tfrac {-2}{10}}}$	0.000 ${\displaystyle {\tfrac {0}{3}}}$	−0.250 ${\displaystyle {\tfrac {-1}{4}}}$	−0.333 ${\displaystyle {\tfrac {-1}{3}}}$
W4A ZF 4HP 18	4[d] 4[d]	Late Market Position[b]	8 7	3[e] 2[e]	3 2	2 3
Δ Number	0		1	1	1	-1
Relative Δ	0.000 ${\displaystyle {\tfrac {0}{4}}}$	0.000[b] ${\displaystyle {\tfrac {0}{4}}:{\tfrac {1}{7}}={\tfrac {0}{4}}\cdot {\tfrac {7}{1}}={\tfrac {0}{4}}}$	0.143 ${\displaystyle {\tfrac {1}{7}}}$	0.500 ${\displaystyle {\tfrac {1}{2}}}$	0.500 ${\displaystyle {\tfrac {1}{2}}}$	−0.333 ${\displaystyle {\tfrac {-1}{3}}}$
W4A 3-Speed[f]	4[d] 3[d]	Historical Market Position[b]	8 7	3[e] 2	3 3	2 2
Δ Number	1		1	1	0	0
Relative Δ	0.333 ${\displaystyle {\tfrac {1}{3}}}$	2.333[b] ${\displaystyle {\tfrac {1}{3}}:{\tfrac {1}{7}}={\tfrac {1}{3}}\cdot {\tfrac {7}{1}}={\tfrac {7}{3}}}$	0.143 ${\displaystyle {\tfrac {1}{7}}}$	0.500 ${\displaystyle {\tfrac {1}{2}}}$	0.000 ${\displaystyle {\tfrac {0}{3}}}$	0.000 ${\displaystyle {\tfrac {0}{2}}}$
^ Progress increases cost-effectiveness and is reflected in the ratio of forward gears to main components. It depends on the power flow: parallel: using the two degrees of freedom of planetary gearsets to increase the number of gears with unchanged number of components serial: in-line combined planetary gearsets without using the two degrees of freedom to increase the number of gears a corresponding increase in the number of components is unavoidable ^ a b c d e f g h i j Innovation Elasticity Classifies Progress And Market Position Automobile manufacturers drive forward technical developments primarily in order to remain competitive or to achieve or defend technological leadership. This technical progress has therefore always been subject to economic constraints Only innovations whose relative additional benefit is greater than the relative additional resource input, i.e. whose economic elasticity is greater than 1, are considered for realization The required innovation elasticity of an automobile manufacturer depends on its expected return on investment. The basic assumption that the relative additional benefit must be at least twice as high as the relative additional resource input helps with orientation negative, if the output increases and the input decreases, is perfect 2 or above is good 1 or above is acceptable (red) below this is unsatisfactory (bold) ^ Direct Predecessor To reflect the progress of the specific model change ^ a b c d e f g h plus 1 reverse gear ^ a b c d e of which 2 gearsets are combined as a compound Ravigneaux gearset ^ Historical Reference Standard (Benchmark) 3-speed transmissions with torque converters have established the modern market for automatic transmissions and thus made it possible in the first place, as this design proved to be a particularly successful compromise between cost and performance It became the archetype and dominated the world market for around 3 decades, setting the standard for automatic transmissions. It was only when fuel consumption became the focus of interest that this design reached its limits, which is why it has now completely disappeared from the market What has remained is the orientation that it offers as a reference standard (point of reference, benchmark) for this market for determining progressiveness and thus the market position of all other, later designs All transmission variants consist of 7 main components Typical examples are Turbo-Hydramatic from GM Cruise-O-Matic from Ford TorqueFlite from Chrysler Detroit Gear from BorgWarner for Studebaker BW-35 from BorgWarner and as T35 from Aisin 3N 71 from Nissan/Jatco 3 HP from ZF Friedrichshafen W3A 040 and W3B 050 from Mercedes-Benz

The need of 2 housings^[a] and 2 different controls^[b] turn out the W5A 030 as the least economically designed automatic transmission ever manufactured for passenger cars. Obviously a transition solution: the direct successor, launched in 1996, requires 9 main components,^[c] 1 housing and 1 control.^[d]

Gearset Concept: Cost-Effectiveness^[e]

With Assessment	Output: Gear Ratios	Innovation Elasticity[f] Δ Output : Δ Input	Input: Main Components
			Total	Gearsets	Brakes	Clutches
W5A Ref. Object	${\displaystyle n_{O1}}$ ${\displaystyle n_{O2}}$	Topic[f]	${\displaystyle n_{I}=n_{G}+}$ ${\displaystyle n_{B}+n_{C}}$	${\displaystyle n_{G1}}$ ${\displaystyle n_{G2}}$	${\displaystyle n_{B1}}$ ${\displaystyle n_{B2}}$	${\displaystyle n_{C1}}$ ${\displaystyle n_{C2}}$
Δ Number	${\displaystyle n_{O1}-n_{O2}}$		${\displaystyle n_{I1}-n_{I2}}$	${\displaystyle n_{G1}-n_{G2}}$	${\displaystyle n_{B1}-n_{B2}}$	${\displaystyle n_{C1}-n_{C2}}$
Relative Δ	Δ Output ${\displaystyle {\tfrac {n_{O1}-n_{O2}}{n_{O2}}}}$	${\displaystyle {\tfrac {n_{O1}-n_{O2}}{n_{O2}}}:{\tfrac {n_{I1}-n_{I2}}{n_{I2}}}}$ ${\displaystyle ={\tfrac {n_{O1}-n_{O2}}{n_{O2}}}\cdot {\tfrac {n_{I2}}{n_{I1}-n_{I2}}}}$	Δ Input ${\displaystyle {\tfrac {n_{I1}-n_{I2}}{n_{I2}}}}$	${\displaystyle {\tfrac {n_{G1}-n_{G2}}{n_{G2}}}}$	${\displaystyle {\tfrac {n_{B1}-n_{B2}}{n_{B2}}}}$	${\displaystyle {\tfrac {n_{C1}-n_{C2}}{n_{C2}}}}$
W5A W4A[g]	5[h] 4[h]	Progress[f]	11 8	4[i] 3[i]	4 3	3 2
Δ Number	1		3	1	1	1
Relative Δ	0.250 ${\displaystyle {\tfrac {1}{4}}}$	0.667[f] ${\displaystyle {\tfrac {1}{4}}:{\tfrac {3}{8}}={\tfrac {1}{4}}\cdot {\tfrac {8}{3}}={\tfrac {2}{3}}}$	0.375 ${\displaystyle {\tfrac {3}{8}}}$	0.333 ${\displaystyle {\tfrac {1}{3}}}$	0.333 ${\displaystyle {\tfrac {1}{3}}}$	0.500 ${\displaystyle {\tfrac {1}{2}}}$
W5A ZF 5HP 18	5[h] 5[h]	Early Market Position[f]	11 10	4[i] 3[i]	4 3	3 4
Δ Number	0		1	1	1	-1
Relative Δ	0.000 ${\displaystyle {\tfrac {0}{5}}}$	0.000[f] ${\displaystyle {\tfrac {0}{5}}:{\tfrac {1}{10}}={\tfrac {0}{5}}\cdot {\tfrac {10}{1}}={\tfrac {0}{1}}}$	0.100 ${\displaystyle {\tfrac {1}{10}}}$	0.333 ${\displaystyle {\tfrac {1}{3}}}$	1.000 ${\displaystyle {\tfrac {2}{2}}}$	−0.250 ${\displaystyle {\tfrac {-1}{4}}}$
W5A ZF 5HP 30	5[h] 5[h]	Late Market Position[f]	11 9	4[i] 3	4 3	3 3
Δ Number	0		2	1	1	0
Relative Δ	0.000 ${\displaystyle {\tfrac {0}{5}}}$	0.000[f] ${\displaystyle {\tfrac {0}{5}}:{\tfrac {2}{9}}={\tfrac {0}{5}}\cdot {\tfrac {9}{2}}={\tfrac {0}{1}}}$	0.222 ${\displaystyle {\tfrac {2}{9}}}$	0.333 ${\displaystyle {\tfrac {1}{3}}}$	0.333 ${\displaystyle {\tfrac {1}{3}}}$	0.000 ${\displaystyle {\tfrac {0}{4}}}$
W5A 3-Speed[j]	5[h] 3[h]	Historical Market Position[f]	11 7	4[i] 2	4 3	3 2
Δ Number	2		4	2	1	1
Relative Δ	0.667 ${\displaystyle {\tfrac {2}{3}}}$	1.167[f] ${\displaystyle {\tfrac {2}{3}}:{\tfrac {4}{7}}={\tfrac {2}{3}}\cdot {\tfrac {7}{4}}={\tfrac {7}{6}}}$	0.571 ${\displaystyle {\tfrac {4}{7}}}$	1.000 ${\displaystyle {\tfrac {2}{2}}}$	0.333 ${\displaystyle {\tfrac {1}{3}}}$	0.500 ${\displaystyle {\tfrac {1}{2}}}$
^ regular bousing for gear 1 to 4 and reverse gear · supplemental housing for gear 5 ^ hydraulic for gear 1 to 4 and reverse gear · electronic for gear 5 ^ 3 simple planetary gearsets, 3 brakes, 3 clutches ^ electronic ^ Progress increases cost-effectiveness and is reflected in the ratio of forward gears to main components. It depends on the power flow: parallel: using the two degrees of freedom of planetary gearsets to increase the number of gears with unchanged number of components serial: in-line combined planetary gearsets without using the two degrees of freedom to increase the number of gears a corresponding increase in the number of components is unavoidable ^ a b c d e f g h i j Innovation Elasticity Classifies Progress And Market Position Automobile manufacturers drive forward technical developments primarily in order to remain competitive or to achieve or defend technological leadership. This technical progress has therefore always been subject to economic constraints Only innovations whose relative additional benefit is greater than the relative additional resource input, i.e. whose economic elasticity is greater than 1, are considered for realization The required innovation elasticity of an automobile manufacturer depends on its expected return on investment. The basic assumption that the relative additional benefit must be at least twice as high as the relative additional resource input helps with orientation negative, if the output increases and the input decreases, is perfect 2 or above is good 1 or above is acceptable (red) below this is unsatisfactory (bold) ^ Direct Predecessor To reflect the progress of the specific model change ^ a b c d e f g h plus 1 reverse gear ^ a b c d e f of which 2 gearsets are combined as a compound Ravigneaux gearset ^ Historical Reference Standard (Benchmark) 3-speed transmissions with torque converters have established the modern market for automatic transmissions and thus made it possible in the first place, as this design proved to be a particularly successful compromise between cost and performance It became the archetype and dominated the world market for around 3 decades, setting the standard for automatic transmissions. It was only when fuel consumption became the focus of interest that this design reached its limits, which is why it has now completely disappeared from the market What has remained is the orientation that it offers as a reference standard (point of reference, benchmark) for this market for determining progressiveness and thus the market position of all other, later designs All transmission variants consist of 7 main components Typical examples are Turbo-Hydramatic from GM Cruise-O-Matic from Ford TorqueFlite from Chrysler Detroit Gear from BorgWarner for Studebaker BW-35 from BorgWarner and as T35 from Aisin 3N 71 from Nissan/Jatco 3 HP from ZF Friedrichshafen W3A 040 and W3B 050 from Mercedes-Benz

The most obvious flaw of the gearset concept is the second gear, which is clearly too short, but this affected all Mercedes-Benz transmissions, especially automatic transmissions.^[2] After Hans-Joachim Foerster, the originator of this flawed gear ratio, left the company in November 1982,^[3] Mercedes-Benz began to address this problem. This led to the introduction of the W4A 040 II with modified gear ratios in 1985. With the 7G-Tronic transmission from 2003, they finally succeeded in completely resolving this issue.

Gear Ratio Analysis

In-Depth Analysis With Assessment[a]		Planetary Gearset: Teeth[b]				Count	Nomi- nal[c] Effec- tive[d]	Cen- ter[e]
		Ravigneaux		Simple				Avg.[f]
Model Type	Version First Delivery	S1[g] R1[h]	S2[i] R2[j]	S3[k] R3[l]	S4[m] R4[n]	Brakes Clutches	Ratio Span	Gear Step[o]
Gear Ratio		R ${\displaystyle {i_{R}}}$		1 ${\displaystyle {i_{1}}}$	2 ${\displaystyle {i_{2}}}$	3 ${\displaystyle {i_{3}}}$	4 ${\displaystyle {i_{4}}}$	5 ${\displaystyle {i_{5}}}$
Step[o]		${\displaystyle -{\frac {i_{R}}{i_{1}}}}$[p]		${\displaystyle {\frac {i_{1}}{i_{1}}}}$	${\displaystyle {\frac {i_{1}}{i_{2}}}}$[q]	${\displaystyle {\frac {i_{2}}{i_{3}}}}$	${\displaystyle {\frac {i_{3}}{i_{4}}}}$	${\displaystyle {\frac {i_{4}}{i_{5}}}}$
Δ Step[r][s]					${\displaystyle {\tfrac {i_{1}}{i_{2}}}:{\tfrac {i_{2}}{i_{3}}}}$	${\displaystyle {\tfrac {i_{2}}{i_{3}}}:{\tfrac {i_{3}}{i_{4}}}}$	${\displaystyle {\tfrac {i_{3}}{i_{4}}}:{\tfrac {i_{4}}{i_{5}}}}$
Shaft Speed		${\displaystyle {\frac {i_{1}}{i_{R}}}}$		${\displaystyle {\frac {i_{1}}{i_{1}}}}$	${\displaystyle {\frac {i_{1}}{i_{2}}}}$	${\displaystyle {\frac {i_{1}}{i_{3}}}}$	${\displaystyle {\frac {i_{1}}{i_{4}}}}$	${\displaystyle {\frac {i_{1}}{i_{5}}}}$
Δ Shaft Speed[t]		${\displaystyle 0-{\tfrac {i_{1}}{i_{R}}}}$		${\displaystyle {\tfrac {i_{1}}{i_{1}}}-0}$	${\displaystyle {\tfrac {i_{1}}{i_{2}}}-{\tfrac {i_{1}}{i_{1}}}}$	${\displaystyle {\tfrac {i_{1}}{i_{3}}}-{\tfrac {i_{1}}{i_{2}}}}$	${\displaystyle {\tfrac {i_{1}}{i_{4}}}-{\tfrac {i_{1}}{i_{3}}}}$	${\displaystyle {\tfrac {i_{1}}{i_{5}}}-{\tfrac {i_{1}}{i_{4}}}}$
Specific Torque[u]		${\displaystyle {\tfrac {T_{2;R}}{T_{1;R}}}}$[v]		${\displaystyle {\tfrac {T_{2;1}}{T_{1;1}}}}$[v]	${\displaystyle {\tfrac {T_{2;2}}{T_{1;2}}}}$[v]	${\displaystyle {\tfrac {T_{2;3}}{T_{1;3}}}}$[v]	${\displaystyle {\tfrac {T_{2;4}}{T_{1;4}}}}$[v]	${\displaystyle {\tfrac {T_{2;5}}{T_{1;5}}}}$[v]
Efficiency ${\displaystyle \eta _{n}}$[u]		${\displaystyle {\tfrac {T_{2;R}}{T_{1;R}}}:{i_{R}}}$		${\displaystyle {\tfrac {T_{2;1}}{T_{1;1}}}:{i_{1}}}$	${\displaystyle {\tfrac {T_{2;2}}{T_{1;2}}}:{i_{2}}}$	${\displaystyle {\tfrac {T_{2;3}}{T_{1;3}}}:{i_{3}}}$	${\displaystyle {\tfrac {T_{2;4}}{T_{1;4}}}:{i_{4}}}$	${\displaystyle {\tfrac {T_{2;5}}{T_{1;5}}}:{i_{5}}}$
W4A 040 I 722.3	40 kp⋅m (289 lb⋅ft) 1979[4][5]	34 50	50 78	34 78		3 2	3.6759 3.6759	1.9173
								1.5433[o]
Gear Ratio		−5.1388[p] ${\displaystyle -{\tfrac {2,184}{425}}}$		3.6759 ${\displaystyle {\tfrac {3,584}{975}}}$	2.4123 [o][s] ${\displaystyle {\tfrac {784}{325}}}$	1.4359[o] ${\displaystyle {\tfrac {56}{39}}}$	1.0000 ${\displaystyle {\tfrac {1}{1}}}$
Step		1.3980[p]		1.0000	1.5238[o]	1.6800[o]	1.4359
Δ Step[r]					0.9070[s]	1.1700
Speed		-0.7153		1.0000	1.5238	2.5600	3.6759
Δ Speed		0.7153		1.0000	0.5238	1.0362	1.1159
Specific Torque[u]		–4.9659 –4.8805		3.6091 3.5758	2.3687 2.3471	1.4272 1.4228	1.0000
Efficiency ${\displaystyle \eta _{n}}$[u]		0.9664 0.9497		0.9818 0.9728	0.9819 0.9730	0.9939 0.9909	1.0000
W4A 020 722.4	20 kp⋅m (145 lb⋅ft) 1982[4][5]	26 42	42 78	38 78		3 2	4.2491 4.2491	2.0613
								1.6197[o]
Gear Ratio		−5.6692[p] ${\displaystyle -{\tfrac {754}{133}}}$		4.2491 ${\displaystyle {\tfrac {1,160}{273}}}$	2.4078[q] ${\displaystyle {\tfrac {1,972}{819}}}$	1.4872 ${\displaystyle {\tfrac {58}{39}}}$	1.0000 ${\displaystyle {\tfrac {1}{1}}}$
Step		1.3342[p]		1.0000	1.7647[q]	1.6190	1.4872
Δ Step[r]					1.0900	1.0887
Speed		-0.7153		1.0000	1.7647	2.8571	4.2491
Δ Speed		0.7153		1.0000	0.7647	1.0924	1.3919
Specific Torque[u]		–5.4811 –5.3882		4.1664 4.1253	2.3647 2.3434	1.4774 1.4726	1.0000
Efficiency ${\displaystyle \eta _{n}}$[u]		0.9668 0.9504		0.9805 0.9709	0.9821 0.9733	0.9934 0.9902	1.0000
W4A 040 II 722.3	40 kp⋅m (289 lb⋅ft) 1985[4]	26 46	46 78	34 78		3 2	3.8707 3.8707	1.9674
								1.5701[o]
Ratio		−5.5857[p]		3.8707	2.2475[q]	1.4359	1.0000
W4A 028 722.3	28 kp⋅m (203 lb⋅ft) 1990[4]	26 46	46 78	34 78		3 2	3.8707	1.9674
								1.5701[o]
Ratio		−5.5857[p]		3.8707	2.2475[q]	1.4359	1.0000
W5A 030 722.5	30 kp⋅m (217 lb⋅ft) 1990[4]	26 46	46 78	34 78	26 78	4 3	5.1609 5.1609	1.7038
								1.5072[o]
Gear Ratio		−5.5857[p] ${\displaystyle -{\tfrac {2,184}{391}}}$		3.8707 ${\displaystyle {\tfrac {3,472}{897}}}$	2.2475[q] ${\displaystyle {\tfrac {672}{299}}}$	1.4359 ${\displaystyle {\tfrac {56}{39}}}$	1.0000 ${\displaystyle {\tfrac {1}{1}}}$	0.7500 ${\displaystyle {\tfrac {3}{4}}}$
Step		1.4431[p]		1.0000	1.7222[q]	1.5652	1.4359	1.3333
Δ Step[r]					1.1003	1.0901	1.0769
Speed		-0.6930		1.0000	1.7222	2.6957	3.8707	5.1609
Δ Speed		0.6930		1.0000	0.7222	0.9734	1.1750	1.2902
Specific Torque[u]		–5.3977 –5.3049		3.7988 3.7631	2.2098 2.1911	1.4272 1.4228	1.0000	0.7462 0.7442
Efficiency ${\displaystyle \eta _{n}}$[u]		0.9664 0.9497		0.9814 0.9722	0.9832 0.9749	0.9939 0.9909	1.0000	0.9949 0.9923
Actuated Shift Elements
Brake A[w]					❶
Brake B[x]				❶	❶	❶
Brake R[y]		❶
Brake S[z]								❶
Clutch E[aa]						❶	❶	❶
Clutch F[ab]		❶		❶			❶	❶
Clutch S[ac]		❶		❶	❶	❶	❶
Geometric Ratios
Ratio R & 3 Ordinary[ad] Elementary Noted[ae]	${\displaystyle {i_{R}}=-{\frac {R_{2}(S_{3}+R_{3})}{S_{2}S_{3}}}}$					${\displaystyle {i_{3}}={\frac {S_{3}+R_{3}}{R_{3}}}}$
	${\displaystyle {i_{R}}=-{\tfrac {R_{2}}{S_{2}}}\left(1+{\tfrac {R_{3}}{S_{3}}}\right)}$					${\displaystyle {i_{3}}=1+{\tfrac {S_{3}}{R_{3}}}}$
Ratio 1 & 4 Ordinary[ad] Elementary Noted[ae]	${\displaystyle {i_{1}}={\frac {(S_{2}+R_{2})(S_{3}+R_{3})}{S_{2}R_{3}}}}$					${\displaystyle {i_{4}}={\frac {1}{1}}}$
	${\displaystyle {i_{1}}=\left(1+{\tfrac {R_{2}}{S_{2}}}\right)\left(1+{\tfrac {S_{3}}{R_{3}}}\right)}$
Ratio 2 & 5 Ordinary[ad] Elementary Noted[ae]	${\displaystyle {i_{2}}={\frac {(S_{1}+R_{1})(S_{3}+R_{3})}{R_{1}R_{3}}}}$					${\displaystyle {i_{5}}={\frac {R_{4}}{S_{4}+R_{4}}}}$
	${\displaystyle {i_{2}}=\left(1+{\tfrac {S_{1}}{R_{1}}}\right)\left(1+{\tfrac {S_{3}}{R_{3}}}\right)}$					${\displaystyle {i_{5}}={\tfrac {1}{1+{\tfrac {S_{4}}{R_{4}}}}}}$
Kinetic Ratios
Specific Torque[u] R & 3	${\displaystyle {\tfrac {T_{2;R}}{T_{1;R}}}=-{\tfrac {R_{2}}{S_{2}}}\eta _{0}\left(1+{\tfrac {R_{3}}{S_{3}}}\eta _{0}\right)}$					${\displaystyle {\tfrac {T_{2;3}}{T_{1;3}}}=1+{\tfrac {S_{3}}{R_{3}}}\eta _{0}}$
Specific Torque[u] 1 & 4	${\displaystyle {\tfrac {T_{2;1}}{T_{1;1}}}=\left(1+{\tfrac {R_{2}}{S_{2}}}\eta _{0}\right)\left(1+{\tfrac {S_{3}}{R_{3}}}\eta _{0}\right)}$					${\displaystyle {\tfrac {T_{2;4}}{T_{1;4}}}={\tfrac {1}{1}}}$
Specific Torque[u] 2 & 5	${\displaystyle {\tfrac {T_{2;2}}{T_{1;2}}}=\left(1+{\tfrac {S_{1}}{R_{1}}}{\eta _{0}}^{\tfrac {3}{2}}\right)\left(1+{\tfrac {S_{3}}{R_{3}}}\eta _{0}\right)}$					${\displaystyle {\tfrac {T_{2;5}}{T_{1;5}}}={\tfrac {1}{1+{\tfrac {S_{4}}{R_{4}}}\cdot {\tfrac {1}{\eta _{0}}}}}}$
^ Revised 9 December 2025 ^ Layout Input and output are on opposite sides Planetary gearset 1 (the inner Ravigneaux gearset) is on the input (turbine) side Input shafts is S2 Output shaft is C3 (the carrier of gearset 3) Output shaft W5A 030 is R4 ^ Total Ratio Span (Total Gear/Transmission Ratio) Nominal ${\displaystyle {\frac {i_{1}}{i_{n}}}}$ A wider span enables the downspeeding when driving outside the city limits increase the climbing ability when driving over mountain passes or off-road or when towing a trailer ^ Total Ratio Span (Total Gear/Transmission Ratio) Effective ${\displaystyle {\frac {min(i_{1};|i_{R}|)}{i_{n}}}}$ The span is only effective to the extent that the reverse gear ratio matches that of 1st gear see also Standard R:1 ^ Ratio Span's Center ${\displaystyle (i_{1}i_{n})^{\frac {1}{2}}}$ The center indicates the speed level of the transmission Together with the final drive ratio it gives the shaft speed level of the vehicle ^ Average Gear Step ${\displaystyle \left({\frac {i_{1}}{i_{n}}}\right)^{\frac {1}{n-1}}}$ With decreasing step width the gears connect better to each other shifting comfort increases ^ Sun 1: sun gear of gearset 1: inner Ravigneaux gearset ^ Ring 1: ring gear of gearset 1: inner Ravigneaux gearset ^ Sun 2: sun gear of gearset 2: outer Ravigneaux gearset ^ Ring 2: ring gear of gearset 2: outer Ravigneaux gearset ^ Sun 3: sun gear of gearset 3 ^ Ring 3: ring gear of gearset 3 ^ Sun 4: sun gear of gearset 4 · W5A 030 only ^ Ring 4: ring gear of gearset 4 · W5A 030 only ^ a b c d e f g h i j k Standard 50:50 — 50 % Is Above And 50 % Is Below The Average Gear Step — With steadily decreasing gear steps (yellow highlighted line Step) and a particularly large step from 1st to 2nd gear the lower half of the gear steps (between the small gears; rounded down, here the first 1 · W5A 030: the first 2) is always larger and the upper half of the gear steps (between the large gears; rounded up, here the last 2) is always smaller than the average gear step (cell highlighted yellow two rows above on the far right) lower half: smaller gear steps are a waste of possible ratios (red bold) upper half: larger gear steps are unsatisfactory (red bold) ^ a b c d e f g h i Standard R:1 — Reverse And 1st Gear Have The Same Ratio — The ideal reverse gear has the same transmission ratio as 1st gear no impairment when maneuvering especially when towing a trailer a torque converter can only partially compensate for this deficiency Plus 11.11 % minus 10 % compared to 1st gear is good Plus 25 % minus 20 % is acceptable (red) Above this is unsatisfactory (bold) see also Total Ratio Span (Total Gear/Transmission Ratio) Effective ^ a b c d e f g Standard 1:2 — Gear Step 1st To 2nd Gear As Small As Possible — With continuously decreasing gear steps (yellow marked line Step) the largest gear step is the one from 1st to 2nd gear, which for a good speed connection and a smooth gear shift must be as small as possible A gear ratio of up to 1.6667 : 1 (5 : 3) is good Up to 1.7500 : 1 (7 : 4) is acceptable (red) Above is unsatisfactory (bold) ^ a b c d From large to small gears (from right to left) ^ a b c Standard STEP — From Large To Small Gears: Steady And Progressive Increase In Gear Steps — Gear steps should increase: Δ Step (first green highlighted line Δ Step) is always greater than 1 As progressive as possible: Δ Step is always greater than the previous step Not progressively increasing is acceptable (red) Not increasing is unsatisfactory (bold) ^ Standard SPEED — From Small To Large Gears: Steady Increase In Shaft Speed Difference — Shaft speed differences should increase: Δ Shaft Speed (second line marked in green Δ (Shaft) Speed) is always greater than the previous one 1 difference smaller than the previous one is acceptable (red) 2 consecutive ones are a waste of possible ratios (bold) ^ a b c d e f g h i j k Specific Torque Ratio And Efficiency The specific torque is the Ratio of output torque ${\displaystyle T_{2;n}}$ to input torque ${\displaystyle T_{1;n}}$ with ${\displaystyle n=gear}$ The efficiency is calculated from the specific torque in relation to the transmission ratio Power loss for single meshing gears is in the range of 1 % to 1.5 % helical gear pairs, which are used to reduce noise in passenger cars, are in the upper part of the loss range spur gear pairs, which are limited to commercial vehicles due to their poorer noise comfort, are in the lower part of the loss range ^ a b c d e f Corridor for specific torque and efficiency in planetary gearsets, the stationary gear ratio ${\displaystyle i_{0}}$ is formed via the planetary gears and thus by two meshes for reasons of simplification, the efficiency for both meshes together is commonly specified there the efficiencies ${\displaystyle \eta _{0}}$ specified here are based on assumed efficiencies for the stationary ratio ${\displaystyle i_{0}}$ of ${\displaystyle \eta _{0}=0.9800}$ (upper value) and ${\displaystyle \eta _{0}=0.9700}$ (lower value) for both interventions together The corresponding efficiency for single-meshing gear pairs is ${\displaystyle {\eta _{0}}^{\frac {1}{2}}}$ at ${\displaystyle 0.9800^{\frac {1}{2}}=0.98995}$ (upper value) and ${\displaystyle 0.9700^{\frac {1}{2}}=0.98489}$ (lower value) ^ Blocks S1 (sun gear of the inner Ravigneaux gearset) ^ Blocks S3 ^ Blocks C1 and C2 (the common Ravigneaux carrier 1 + 2) ^ Blocks S4 (S: german "schnell" for fast) · W5A 030 only ^ Couples S1 (the sun gear of the inner Ravigneaux gearset) with C1 and C2 (the common Ravigneaux carrier 1 + 2) ^ Connects R2 and S3 ^ Couples S4 with R4 (S: german "schnell" for fast) · W5A 030 only ^ a b c Ordinary Noted For direct determination of the ratio ^ a b c Elementary Noted Alternative representation for determining the transmission ratio Contains only operands With simple fractions of both central gears of a planetary gearset Or with the value 1 As a basis For reliable And traceable Determination of specific torque and efficiency

• List of Daimler AG transmissions