Mercedes-Benz 7G-Tronic transmission

7G-Tronic
7G-Tronic
	Mercedes-Benz 7G-Tronic transmission
Overview
Manufacturer	Daimler AG
Model code	W7A 400 · W7A 700 · Type 722.9
Production	2003–2020
Body and chassis
Class	7-speed longitudinal automatic transmission
Related	ZF 6HP · ZF 8HP
Chronology
Predecessor	5G-Tronic
Successor	9G-Tronic

7G-Tronic is Mercedes-Benz's trademark name for its 7-speed automatic transmission type 722.9. It was produced from 2003 to 2020 in different variants as converter-7-gear-automatic transmission (German: Wandler-7-Gang-Automatik). The core models W7A 400 and W7A 700 are for engines up to 400 N⋅m (295 lb⋅ft) or 700 N⋅m (516 lb⋅ft) maximum input torque.

This fifth-generation transmission was the first 7-speed automatic transmission ever used on a production passenger vehicle.^[1] It initially debuted in Autumn 2003 on 5 different V8-cylinder models: the E 500, S 430, S 500, CL 500, and SL 500. It became available on many 6-cylinder models too. Turbocharged V12 engines, 4-cylinder applications and commercial vehicles continued to use the older Mercedes-Benz 5G-Tronic transmission for many years.

The company claims that the 7G-Tronic is more fuel efficient and has shorter acceleration times and quicker intermediate sprints than the outgoing 5-speed automatic transmission.^[1] It has 2 reverse gears.

The transmission can skip gears when downshifting. It also has a torque converter lock-up on all 7 gears, allowing better transmission of torque for improved acceleration. The transmission's casing is made of magnesium alloy, a first for the industry, to save weight.^[2] The 7G-Tronic transmission is built at the Mercedes-Benz Stuttgart-Untertuerkheim plant in Germany, the site of Daimler-Benz's original production facility.

In July 2009, Mercedes-Benz announced they are working on a new nine-speed automatic.^[3]

Gear Ratios^[a]
Model	Type	First Deliv- ery	Gear									Total Span			Avg. Step	Components		Nomenclature
Model	Type	First Deliv- ery	R 2	R 1	1	2	3	4	5	6	7	Nomi- nal	Effec- tive	Cen- ter	Avg. Step	Total	per Gear^[b]	Cou- pling	Gears Count	Ver- sion	Maximum Input Torque

W7A 400 W7A 700 W7A 900	722.9 NAG 2 ^[c]	2003	−2.231	−3.416	4.377	2.859	1.921	1.368	1.000	0.820	0.728	6.016	4.695	1.785	1.349	4 Gearsets 4 Brakes 3 Clutches	1.571	W^[d]	7^[b]	A	400 N⋅m (295 lb⋅ft) 700 N⋅m (516 lb⋅ft) 1,000 N⋅m (738 lb⋅ft)

^ Differences in gear ratios have a measurable, direct impact on vehicle dynamics, performance, waste emissions as well as fuel mileage ^ ^a ^b Forward gears only ^ 2nd generation of advanced automatic transmissions, at Mercedes-Benz referred to as NAG 2 (New Automatic Gearbox Generation 2 · German: Neue Automatikgetriebe-Generation 2)^[4] ^ Torque converter · German: Wandler or Drehmomentwandler

Specifications

Operating Modes

Regular

In normal condition it sequentially shift gears, but if required it can skip some gears, that are: 7 to 5, 6 to 2, 5 to 3 and 3 to 1.^[5] On vehicles with 6 or 8 cylinder engines with comfort mode engaged, as well as on off-road vehicles with low range selected, the transmission will always use 2nd gear as initial gear.^[6]

„Limp-Home Mode“

If the transmission control unit senses a critical fault during driving, it will activate an emergency operating mode: Upon hydraulic failures, it will stop shifting gears and permanently retain the currently selected gear; if the failure can be pinpointed to one of the internal hydraulic control valves, the transmission will continue shifting but stop using the affected gear(s). Upon electrical failure, the transmission shifts to 6th gear. If the critical fault persists after the vehicle is stopped and the engine restarted, only 2nd gear and reverse gear #2 are available.^[5]

AMG SpeedShift

AMG SpeedShift TCT

The TCT transmission is essentially the 7G-Tronic automatic transmission including "Torque Converter Technology". Sporty, performance-oriented version with the same gear ratios. First used in 2005 Mercedes-Benz SLK 55 AMG.^[7] In 2007, 7G-Tronic transmission with AMG SpeedShift was also called '7G-Tronic Sport'.^[8]

AMG SpeedShift MCT

Mercedes-AMG developed the 7-speed MCT "Multi Clutch Technology" planetary automatic transmission. The MCT transmission is essentially the 7G-Tronic automatic transmission without a torque converter. Instead of a torque converter, it uses a compact wet startup clutch to launch the car from a stop and also supports computer-controlled double-clutching. The MCT (Multi-Clutch Technology) acronym refers to a planetary (automatic) transmission's multiple clutches and bands for each gear.^[9]

The MCT is fitted with 4 drive modes: "C" (Comfort), "S" (Sport), "S+" (Sport plus) and "M" (Manual) and boasts 0.1 second shifts in "M" and "S+" modes. MCT-equipped cars are also fitted with the new AMG Drive Unit with an innovative Race Start function. The AMG Drive Unit is the central control unit for the AMG SpeedShift MCT 7-speed sports transmission and all driving dynamics functions. The driver can change gears either using the selector lever or by nudging the steering-wheel shift paddles. The new Race start Function is a launch control system that enables the driver to call on maximum acceleration while ensuring optimum traction of the driven wheels.

It is available on the 2009 SL 63 AMG and E 63 AMG, and will be used for the 2011 S 63 AMG and CL 63 AMG, and the 2012 CLS 63 AMG and C 63 AMG. Compulsory on the 2014 CLS 63 and E 63 AMG models, as well as their "S--Model" variants. Improved with the release of the 2015 model year, by decreasing the lag time between shifts.

Combined Parallel and Serial Coupled Gearset Concept For More Gears And Improved Cost-Effectiveness

This is Mercedes-Benz second generation of advanced automatic transmissions. The design is more advanced than its direct predecessor, but significantly less economical than its competitors. Since Mercedes can charge higher prices than many of its competitors, it was possible to include the 7G-Tronic in the range. With its all new parallel power flow the W7A is referred to at Mercedes-Benz as NAG 2 (New Automatic Gearbox Generation, starting with type 722.6 as generation 1 and continuing with type 722.9 as generation 2).^[4]

Gearset Concept: Cost-Effectiveness^[a]
With Assessment	Output: Gear Ratios	Innovation Elasticity^[b] Δ Output : Δ Input	Input: Main Components
With Assessment	Output: Gear Ratios	Innovation Elasticity^[b] Δ Output : Δ Input	Total	Gearsets	Brakes	Clutches

W7A Ref. Object	$n_{O1}$ $n_{O2}$	Topic^[b]	$n_{I}=n_{G}+$ $n_{B}+n_{C}$	$n_{G1}$ $n_{G2}$	$n_{B1}$ $n_{B2}$	$n_{C1}$ $n_{C2}$
Δ Number	$n_{O1}-n_{O2}$	Topic^[b]	$n_{I1}-n_{I2}$	$n_{G1}-n_{G2}$	$n_{B1}-n_{B2}$	$n_{C1}-n_{C2}$
Relative Δ	Δ Output ${\tfrac {n_{O1}-n_{O2}}{n_{O2}}}$	${\tfrac {n_{O1}-n_{O2}}{n_{O2}}}:{\tfrac {n_{I1}-n_{I2}}{n_{I2}}}$ $={\tfrac {n_{O1}-n_{O2}}{n_{O2}}}\cdot {\tfrac {n_{I2}}{n_{I1}-n_{I2}}}$	Δ Input ${\tfrac {n_{I1}-n_{I2}}{n_{I2}}}$	${\tfrac {n_{G1}-n_{G2}}{n_{G2}}}$	${\tfrac {n_{B1}-n_{B2}}{n_{B2}}}$	${\tfrac {n_{C1}-n_{C2}}{n_{C2}}}$

W7A W5A^[c]	7^[d] 5^[d]	Progress^[b]	11^[10]^[5]^[11] 9	4^[e] 3	4 3	3 3
Δ Number	2	Progress^[b]	2	1	1	0
Relative Δ	0.400 ${\tfrac {2}{5}}$	1.800^[b] ${\tfrac {2}{5}}:{\tfrac {2}{9}}={\tfrac {2}{5}}\cdot {\tfrac {9}{2}}={\tfrac {9}{5}}$	0.222 ${\tfrac {2}{9}}$	0.333 ${\tfrac {1}{3}}$	0.333 ${\tfrac {1}{3}}$	0.000 ${\tfrac {0}{3}}$

W7A ZF 8HP^[f]	7^[d] 8^[g]	Late Market Position^[b]	11 9	4^[e] 4	4 3	3 2
Δ Number	-1	Late Market Position^[b]	-2	0	-1	-1
Relative Δ	−0.125 ${\tfrac {-1}{8}}$	−0.562^[b] ${\tfrac {-1}{8}}:{\tfrac {2}{9}}={\tfrac {-1}{8}}\cdot {\tfrac {9}{2}}={\tfrac {-9}{16}}$	0.222 ${\tfrac {2}{9}}$	0.000 ${\tfrac {0}{4}}$	0.333 ${\tfrac {1}{3}}$	0.500 ${\tfrac {1}{2}}$

W7A ZF 6HP^[h]	7^[d] 6^[g]	Early Market Position^[b]	11 8	4^[e] 3^[e]	4 2	3 3
Δ Number	1	Early Market Position^[b]	3	1	2	0
Relative Δ	0.167 ${\tfrac {1}{6}}$	0.444^[b] ${\tfrac {1}{6}}:{\tfrac {3}{8}}={\tfrac {1}{6}}\cdot {\tfrac {8}{3}}={\tfrac {4}{9}}$	0.375 ${\tfrac {3}{8}}$	0.333 ${\tfrac {1}{3}}$	1.000 ${\tfrac {2}{2}}$	0.000 ${\tfrac {0}{3}}$

W7A 3-Speed^[i]	7^[d] 3^[g]	Historical Market Position^[b]	11 7	4 2	4 3	3 2
Δ Number	4	Historical Market Position^[b]	4	2	1	1
Relative Δ	1.333 ${\tfrac {4}{3}}$	2.333^[b] ${\tfrac {4}{3}}:{\tfrac {4}{7}}={\tfrac {4}{3}}\cdot {\tfrac {7}{4}}={\tfrac {7}{3}}$	0.571 ${\tfrac {4}{7}}$	1.00 ${\tfrac {2}{2}}$	0.333 ${\tfrac {1}{3}}$	0.500 ${\tfrac {1}{2}}$

^ 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 plus 2 reverse gears ^ ^a ^b ^c ^d of which 2 gearsets are combined as a compound Ravigneaux gearset ^ Reference Standard (Benchmark) In 2008 the 8HP became the new reference standard (benchmark) for automatic transmissions ^ ^a ^b ^c plus 1 reverse gear ^ Reference Standard (Benchmark) at that time The 6HP became the new reference standard (benchmark) for automatic transmissions at that time ^ 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

Gearset Concept: Quality

The W7A uses no bands nor sprag clutches.^[5] It is fully electronic controlled. Torque converter lock-up can operate in all 7 forward gears.^[5]

As shown in the assessment table below, the biggest weakness of the gearset concept is the two consecutive reductions in speed increase in 6th and 7th gear.

Gear Ratio Analysis^[a]
In-Depth Analysis^[b] With Assessment And Torque Ratio^[c] And Efficiency Calculation^[d]				Planetary Gear Set: Teeth^[e]				Count	Nomi- nal^[f] Effec- tive^[g]	Cen- ter^[h]
				Ravigneaux		Simple		Count	Nomi- nal^[f] Effec- tive^[g]	Avg.^[i]

Model Type	Version First Delivery			S₁^[j] R₁^[k]	S₂^[l] R₂^[m]	S₃^[n] R₃^[o]	S₄^[p] R₄^[q]	Brakes Clutches	Gear Ratio Span	Gear Step^[r]
Gear Ratio^[b]	R 3^[s] ${i_{R3}}$ ^[b]	R 2 ${i_{R2}}$ ^[b]	R 1 ${i_{R}}$ ^[b]	1 ${i_{1}}$ ^[b]	2 ${i_{2}}$ ^[b]	3 ${i_{3}}$ ^[b]	4 ${i_{4}}$ ^[b]	5 ${i_{5}}$ ^[b]	6 ${i_{6}}$ ^[b]	7 ${i_{7}}$ ^[b]
Step^[r]	$\color {grey}{\frac {i_{R2}}{i_{R3}}}$	${\frac {i_{R1}}{i_{R2}}}$	$-{\frac {i_{R1}}{i_{1}}}$ ^[t]	${\frac {i_{1}}{i_{1}}}$	${\frac {i_{1}}{i_{2}}}$ ^[u]	${\frac {i_{2}}{i_{3}}}$	${\frac {i_{3}}{i_{4}}}$	${\frac {i_{4}}{i_{5}}}$	${\frac {i_{5}}{i_{6}}}$	${\frac {i_{6}}{i_{7}}}$
Δ Step^[v]^[w]		$\color {grey}{\tfrac {i_{R1}}{i_{R2}}}:{\tfrac {i_{R2}}{i_{R3}}}$			${\tfrac {i_{1}}{i_{2}}}:{\tfrac {i_{2}}{i_{3}}}$	${\tfrac {i_{2}}{i_{3}}}:{\tfrac {i_{3}}{i_{4}}}$	${\tfrac {i_{3}}{i_{4}}}:{\tfrac {i_{4}}{i_{5}}}$	${\tfrac {i_{4}}{i_{5}}}:{\tfrac {i_{5}}{i_{6}}}$	${\tfrac {i_{5}}{i_{6}}}:{\tfrac {i_{6}}{i_{7}}}$
Shaft Speed	$\color {grey}{\frac {i_{1}}{i_{R3}}}$	${\frac {i_{1}}{i_{R2}}}$	${\frac {i_{1}}{i_{R1}}}$	${\frac {i_{1}}{i_{1}}}$	${\frac {i_{1}}{i_{2}}}$	${\frac {i_{1}}{i_{3}}}$	${\frac {i_{1}}{i_{4}}}$	${\frac {i_{1}}{i_{5}}}$	${\frac {i_{1}}{i_{6}}}$	${\frac {i_{1}}{i_{7}}}$
Δ Shaft Speed^[x]	$\color {grey}{\tfrac {i_{1}}{i_{R2}}}-{\tfrac {i_{1}}{i_{R3}}}$	${\tfrac {i_{1}}{i_{R1}}}-{\tfrac {i_{1}}{i_{R2}}}$	$0-{\tfrac {i_{1}}{i_{R1}}}$	${\tfrac {i_{1}}{i_{1}}}-0$	${\tfrac {i_{1}}{i_{2}}}-{\tfrac {i_{1}}{i_{1}}}$	${\tfrac {i_{1}}{i_{3}}}-{\tfrac {i_{1}}{i_{2}}}$	${\tfrac {i_{1}}{i_{4}}}-{\tfrac {i_{1}}{i_{3}}}$	${\tfrac {i_{1}}{i_{5}}}-{\tfrac {i_{1}}{i_{4}}}$	${\tfrac {i_{1}}{i_{6}}}-{\tfrac {i_{1}}{i_{5}}}$	${\tfrac {i_{1}}{i_{7}}}-{\tfrac {i_{1}}{i_{6}}}$
Torque Ratio^[c]	$\color {grey}\mu _{R3}$ ^[c]	$\mu _{R2}$ ^[c]	$\mu _{R1}$ ^[c]	$\mu _{1}$ ^[c]	$\mu _{2}$ ^[c]	$\mu _{3}$ ^[c]	$\mu _{4}$ ^[c]	$\mu _{5}$ ^[c]	$\mu _{6}$ ^[c]	$\mu _{7}$ ^[c]
Efficiency $\eta _{n}$ ^[d]	$\color {grey}{\frac {\mu _{R2}}{i_{R2}}}$ ^[d]	${\frac {\mu _{R2}}{i_{R2}}}$ ^[d]	${\frac {\mu _{R1}}{i_{R1}}}$ ^[d]	${\frac {\mu _{1}}{i_{1}}}$ ^[d]	${\frac {\mu _{2}}{i_{2}}}$ ^[d]	${\frac {\mu _{3}}{i_{3}}}$ ^[d]	${\frac {\mu _{4}}{i_{4}}}$ ^[d]	${\frac {\mu _{5}}{i_{5}}}$ ^[d]	${\frac {\mu _{6}}{i_{6}}}$ ^[d]	${\frac {\mu _{7}}{i_{7}}}$ ^[d]

W7A 400 W7A 700 W7A 900 722.9	400 N⋅m (295 lb⋅ft) 700 N⋅m (516 lb⋅ft) 1,000 N⋅m (738 lb⋅ft) NAG 2^[y] · 2003^[10]^[11]			42 86	86 110	28 76	46 114	4 3	6.0162 4.6948 ^[g]^[t]	1.7846
W7A 400 W7A 700 W7A 900 722.9				42 86	86 110	28 76	46 114	4 3	6.0162 4.6948 ^[g]^[t]	1.3486^[r]
Gear Ratio^[c]	−1.4987^[s] $\color {grey}{\tfrac {598}{399}}$	−2.2307 ${\tfrac {38,272}{17,157}}$	−3.4157 ^[t]^[g] $-{\tfrac {8,372}{2,451}}$	4.3772 ${\tfrac {203,840}{46,569}}$	2.8586^[w] ${\tfrac {133,120}{46,569}}$	1.9206 ${\tfrac {2,080}{1,083}}$	1.3684^[w] ${\tfrac {26}{19}}$	1.0000^[r] ${\tfrac {1}{1}}$	0.8204^[x] ${\tfrac {38,272}{46,651}}$	0.7276^[x] ${\tfrac {8,372}{11,507}}$
Step	1.4884	1.5313	0.7804^[t]	1.0000	1.5313	1.4884	1.4035	1.3684^[r]	1.2189	1.1276
Δ Step^[v]		1.0288			1.0288^[w]	1.0605	1.0256^[w]	1.1226	1.0810
Speed	–2.9205	–1.9622	–1.2815	1.0000	1.5313	2.2791	3.1987	4.3772	5.3355	6.0162
Δ Speed	0.9583	0.6808	1.2815	1.0000	0.5313	0.7478	0.9196	1.1785	0.9583^[x]	0.6808^[x]
Torque Ratio^[c]	–1.4473 –1.4219	–2.1400 –2.0955	–3.2433 –3.1594	4.2560 4.1965	2.8083 2.7833	1.8993 1.8886	1.3611 1.3574	1.0000	0.8131 0.8094	0.7179 0.7130
Efficiency $\eta _{n}$ ^[d]	0.9657 0.9487	0.9593 0.9394	0.9495 0.9250	0.9723 0.9587	0.9824 0.9737	0.9889 0.9834	0.9946 0.9919	1.0000	0.9912 0.9866	0.9868 0.9799

Actuated Shift Elements^[z]
Brake 1^[aa]		❶			❶				❶
Brake 2^[ab]				❶	❶	❶	❶
Brake 3^[ac]			❶	❶						❶
Brake BR^[ad]	❶^[s]	❶	❶
Clutch 1^[ae]	❶^[s]					❶	❶	❶
Clutch 2^[af]							❶	❶	❶	❶
Clutch 3^[ag]	❶^[s]	❶	❶	❶	❶	❶		❶	❶	❶
Geometric Ratios: Speed Conversion
Gear Ratio^[b] R3^[s] & R2 & 5 Ordinary^[ah] Elementary Noted^[ai]	$\color {grey}i_{R3}=-{\frac {S_{4}(S_{3}+R_{3})}{S_{3}R_{4}}}$ ^[s]				$i_{R2}=-{\frac {S_{4}(S_{1}+R_{1})(S_{3}+R_{3})}{R_{1}S_{3}R_{4}}}$				$i_{5}={\frac {1}{1}}$
	$\color {grey}i_{R3}=-\left(1+{\tfrac {R_{3}}{S_{3}}}\right){\tfrac {S_{4}}{R_{4}}}$ ^[s]				$i_{R2}=-\left(1+{\tfrac {S_{1}}{R_{1}}}\right)\left(1+{\tfrac {R_{3}}{S_{3}}}\right){\tfrac {S_{4}}{R_{4}}}$				$i_{5}={\frac {1}{1}}$

Gear Ratio^[b] R1 & 1 Ordinary^[ah] Elementary Noted^[ai]	$i_{R1}=-{\frac {S_{4}(S_{2}+R_{2})(S_{3}+R_{3})}{S_{2}S_{3}R_{4}}}$					$i_{1}={\frac {(S_{2}+R_{2})(S_{3}+R_{3})(S_{4}+R_{4})}{S_{2}R_{3}R_{4}}}$
Gear Ratio^[b] R1 & 1 Ordinary^[ah] Elementary Noted^[ai]	$i_{R1}=-\left(1+{\tfrac {R_{2}}{S_{2}}}\right)\left(1+{\tfrac {R_{3}}{S_{3}}}\right){\tfrac {S_{4}}{R_{4}}}$					$i_{1}=\left(1+{\tfrac {R_{2}}{S_{2}}}\right)\left(1+{\tfrac {S_{3}}{R_{3}}}\right)\left(1+{\tfrac {S_{4}}{R_{4}}}\right)$

Gear Ratio^[b] 2–4 Ordinary^[ah] Elementary Noted^[ai]	$i_{2}={\frac {(S_{1}+R_{1})(S_{3}+R_{3})(S_{4}+R_{4})}{R_{1}R_{3}R_{4}}}$					$i_{3}={\frac {(S_{3}+R_{3})(S_{4}+R_{4})}{R_{3}R_{4}}}$			$i_{4}={\frac {S_{3}+R_{3}}{R_{3}}}$
Gear Ratio^[b] 2–4 Ordinary^[ah] Elementary Noted^[ai]	$i_{2}=\left(1+{\tfrac {S_{1}}{R_{1}}}\right)\left(1+{\tfrac {S_{3}}{R_{3}}}\right)\left(1+{\tfrac {S_{4}}{R_{4}}}\right)$					$i_{3}=\left(1+{\tfrac {S_{3}}{R_{3}}}\right)\left(1+{\tfrac {S_{4}}{R_{4}}}\right)$			$i_{4}=1+{\tfrac {S_{3}}{R_{3}}}$

Gear Ratio^[b] 6 & 7 Ordinary^[ah] Elementary Noted^[ai]	$i_{6}={\frac {S_{4}(S_{1}+R_{1})(S_{3}+R_{3})}{S_{4}(S_{1}+R_{1})(S_{3}+R_{3})+S_{1}S_{3}R_{4}}}$					$i_{7}={\frac {S_{4}(S_{2}+R_{2})(S_{3}+R_{3})}{S_{4}(S_{2}+R_{2})(S_{3}+R_{3})+R_{2}S_{3}R_{4}}}$
Gear Ratio^[b] 6 & 7 Ordinary^[ah] Elementary Noted^[ai]	$i_{6}={\tfrac {1}{1+{\tfrac {\tfrac {R_{4}}{S_{4}}}{\left(1+{\tfrac {R_{1}}{S_{1}}}\right)\left(1+{\tfrac {R_{3}}{S_{3}}}\right)}}}}$					$i_{7}={\tfrac {1}{1+{\tfrac {\tfrac {R_{4}}{S_{4}}}{\left(1+{\tfrac {S_{2}}{R_{2}}}\right)\left(1+{\tfrac {R_{3}}{S_{3}}}\right)}}}}$
Kinetic Ratios: Torque Conversion
Torque Ratio^[c] R3^[s] & R2 & 5	$\color {grey}\mu _{R3}=-\left(1+{\tfrac {R_{3}}{S_{3}}}\eta _{0}\right){\tfrac {S_{4}}{R_{4}}}{\eta _{0}}$ ^[s]				$\mu _{R2}=-\left(1+{\tfrac {S_{1}}{R_{1}}}\eta _{0}\right)\left(1+{\tfrac {R_{3}}{S_{3}}}\eta _{0}\right){\tfrac {S_{4}}{R_{4}}}\eta _{0}$				$\mu _{5}{T_{1;5}}={\tfrac {1}{1}}$

Torque Ratio^[c] R1 & 1	$\mu _{R1}=-\left(1+{\tfrac {R_{2}}{S_{2}}}{\eta _{0}}^{\tfrac {3}{2}}\right)\left(1+{\tfrac {R_{3}}{S_{3}}}\eta _{0}\right){\tfrac {S_{4}}{R_{4}}}\eta _{0}$ ^[aj]					$\mu _{1}=\left(1+{\tfrac {R_{2}}{S_{2}}}{\eta _{0}}^{\tfrac {3}{2}}\right)\left(1+{\tfrac {S_{3}}{R_{3}}}\eta _{0}\right)\left(1+{\tfrac {S_{4}}{R_{4}}}\eta _{0}\right)$ ^[aj]

! Torque Ratio^[c] 2–4	$\mu _{2}=\left(1+{\tfrac {S_{1}}{R_{1}}}\eta _{0}\right)\left(1+{\tfrac {S_{3}}{R_{3}}}\eta _{0}\right)\left(1+{\tfrac {S_{4}}{R_{4}}}\eta _{0}\right)$					$\mu _{3}=\left(1+{\tfrac {S_{3}}{R_{3}}}\eta _{0}\right)\left(1+{\tfrac {S_{4}}{R_{4}}}\eta _{0}\right)$			$\mu _{4}=1+{\tfrac {S_{3}}{R_{3}}}\eta _{0}$

! Torque Ratio^[c] 6 & 7	$\mu _{6}={\tfrac {1}{1+{\tfrac {{\tfrac {R_{4}}{S_{4}}}\cdot {\tfrac {1}{\eta _{0}}}}{\left(1+{\tfrac {R_{1}}{S_{1}}}\eta _{0}\right)\left(1+{\tfrac {R_{3}}{S_{3}}}\eta _{0}\right)}}}}$					$\mu _{7}={\tfrac {1}{1+{\tfrac {{\tfrac {R_{4}}{S_{4}}}\cdot {\tfrac {1}{\eta _{0}}}}{\left(1+{\tfrac {S_{2}}{R_{2}}}{\eta _{0}}^{\tfrac {3}{2}}\right)\left(1+{\tfrac {R_{3}}{S_{3}}}\eta _{0}\right)}}}}$ ^[aj]

^ Revised 14 January 2026 Nomenclature $S_{n}=$ sun gear: number of teeth $R_{n}=$ ring gear: number of teeth $\color {gray}{C_{n}=}$ carrier or planetary gear carrier (not needed) $s_{n}=$ sun gear: shaft speed $r_{n}=$ ring gear: shaft speed $c_{n}=$ carrier or planetary gear carrier: shaft speed With $n=$ gear is $i_{n}=$ gear ratio or transmission ratio $\omega _{1;n}=\omega _{t}=$ shaft speed shaft 1: input (turbine) shaft $\omega _{2;n}=$ shaft speed shaft 2: output shaft $T_{1;n}=T_{t}=$ torque shaft 1: input (turbine) shaft $T_{2;n}=$ torque shaft 2: output shaft $\mu _{n}=$ torque ratio or torque conversion ratio $\eta _{n}=$ efficiency $i_{0}=$ stationary gear ratio $\eta _{0}=$ (assumed) stationary gear efficiency ^ ^a ^b ^c ^d ^e ^f ^g ^h ⁱ ^j ^k ^l ^m ⁿ ^o ^p Gear Ratio (Transmission Ratio) $i_{n}$ — Speed Conversion — The gear ratio $i_{n}$ is the ratio of input shaft speed $\omega _{1;n}$ to output shaft speed $\omega _{2;n}$ and therefore corresponds to the reciprocal of the shaft speeds $i_{n}={\frac {1}{\frac {\omega _{2;n}}{\omega _{1;n}}}}={\frac {\omega _{1;n}}{\omega _{2;n}}}={\frac {\omega _{t}}{\omega _{2;n}}}$ ^ ^a ^b ^c ^d ^e ^f ^g ^h ⁱ ^j ^k ^l ^m ⁿ ^o ^p ^q ^r Torque Ratio (Torque Conversion Ratio) $\mu _{n}$ — Torque Conversion — The torque ratio $\mu _{n}$ is the ratio of output torque $T_{2;n}$ to input torque $T_{1;n}$ minus efficiency losses and therefore corresponds (apart from the efficiency losses) to the reciprocal of the shaft speeds too $\mu _{n}=i_{n}\eta _{n;\eta _{0}}={\frac {\omega _{1;n}\eta _{n;\eta _{0}}}{\omega _{2;n}}}={\frac {T_{2;n}\eta _{n;\eta _{0}}}{T_{1;n}}}$ whereby $\eta _{n;\eta _{0}}$ may vary from gear to gear according to the formulas listed in this table and $0\leq \eta _{n;\eta _{0}}\leq 1$ ^ ^a ^b ^c ^d ^e ^f ^g ^h ⁱ ^j ^k ^l ^m Efficiency The efficiency $\eta _{n}$ is calculated from the torque ratio in relation to the gear ratio (transmission ratio) $\eta _{n}={\frac {\mu _{n}}{i_{n}}}$ 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 Corridor for torque ratio and efficiency in planetary gearsets, the stationary gear ratio $i_{0}$ 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 $\eta _{0}$ specified here are based on assumed efficiencies for the stationary ratio $i_{0}$ of $\eta _{0}=0.9800$ (upper value) and $\eta _{0}=0.9700$ (lower value) for both interventions together The corresponding efficiency for single-meshing gear pairs is ${\eta _{0}}^{\tfrac {1}{2}}$ at $0.9800^{\tfrac {1}{2}}=0.98995$ (upper value) and $0.9700^{\tfrac {1}{2}}=0.98489$ (lower value) ^ Layout Input and output are on opposite sides Planetary gearset 2 (the outer Ravigneaux gearset) is on the input (turbine) side Input (turbine) shafts are R₁ and, if actuated, R₃ Output shaft is C₃ ^ Total Ratio Span (Total Gear Ratio/Total Transmission Ratio) Nominal ${\frac {\omega _{2;n}}{\omega _{2;1}}}={\frac {\frac {1}{\omega _{2;1}}}{\frac {1}{\omega _{2;n}}}}={\frac {\frac {\omega _{t}}{\omega _{2;1}}}{\frac {\omega _{t}}{\omega _{2;n}}}}={\frac {i_{1}}{i_{n}}}$ 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 ^ ^a ^b ^c Total Ratio Span (Total Gear Ratio/Total Transmission Ratio) Effective ${\frac {min(i_{1};\|i_{R}\|)}{i_{n}}}$ The span is only effective to the extent that the reverse gear ratio matches that of 1st gear see also Standard R:1 Since reverse gear is usually longer than first gear, the effective span is of central importance for describing the suitability of a transmission. In these cases, the nominal span conveys a misleading picture that is only unproblematic for vehicles with high specific power. Manufacturers naturally have no interest in specifying the effective span. Users have not yet formulated the practical benefits that effective span has for them. Effective span has not yet played a role in research and teaching. Contrary to its importance, effective span has therefore not been able to establish itself in either theory or practice. It is to be hoped that it will find wider application in the future. ^ Ratio Span's Center $(i_{1}i_{n})^{\frac {1}{2}}$ 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 $\left({\frac {i_{1}}{i_{n}}}\right)^{\frac {1}{n-1}}$ 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 ^ Ring 4: ring gear of gearset 4 ^ ^a ^b ^c ^d ^e 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 3) is always larger and the upper half of the gear steps (between the large gears; rounded up, here the last 3) 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 ^j In line with the logic for the 2nd reverse gear of the predecessor 5G-Tronic, the extended layout provides this 3rd reverse gear, but it was not used in the transmission that was finally launched on the market ^ ^a ^b ^c ^d 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 ^ 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 From large to small gears (from right to left) ^ ^a ^b ^c ^d ^e 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) ^ ^a ^b ^c ^d ^e 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) ^ 2nd generation of advanced automatic transmissions, at Mercedes-Benz referred to as NAG 2 (New Automatic Gearbox Generation 2 · German: Neue Automatikgetriebe-Generation 2)^[4] ^ Permanently coupled elements C₁/C₂ (the common carrier of the compound Ravigneaux gearset), and R₄ R₃ and C₄ ^ Blocks S₁ (sun gear of the inner Ravigneaux geaset) ^ Blocks S₃ ^ Blocks R₂ (ring gear of the outer Ravigneaux gearset) ^ Blocks R₃ and C₄ ^ Couples S₁ (sun gear of inner Ravigneaux gearset) with R₂ (ring gear of outer Ravigneaux gearset) ^ Couples R₁ (ring of inner Ravigneaux gearset) with R₃ and C₄ ^ Couples S₃ with S₄ ^ ^a ^b ^c ^d Ordinary Noted For direct determination of the gear ratio ^ ^a ^b ^c ^d 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 the torque ratio and efficiency ^ ^a ^b ^c Power flow in gearset 2 (the outer Ravigneaux gearset) the ring gear 1 driven by the turbine acts like an inverted sun gear 1 with the size of sun gear 2 this results in the following power flow: $R_{1}\Rightarrow Pinions_{1}\Rightarrow Pinions_{2}\Rightarrow R_{2}$ this three meshings are reflected in the exponent of the term for efficiency ${\tfrac {R_{2}}{S_{2}}}{\eta _{0}}^{\tfrac {3}{2}}$ or ${\tfrac {S_{2}}{R_{2}}}{\eta _{0}}^{\tfrac {3}{2}}$ nevertheless, all gear dimensions of gear set 1 can be shortened completely

Applications

Mercedes models

Mercedes C-Class

2005–2007 Mercedes-Benz W203 (C 320 CDI, C 230, C 280, C 350; post-facelift)
2005–2007 Mercedes-Benz CL203 (C 230 Sport Coupé, C 350 Sport Coupé; post-facelift), (CLC 250, CLC 350)
2007–2011 Mercedes-Benz C-Class (W204) (C 320 CDI)
2011–2018 Mercedes-Benz W204 (C 63 AMG, C 63 AMG Black Series)
2014 Mercedes-Benz W205 (C 180)

Mercedes E-Class

2009–2016 Mercedes-Benz W212 (E 200 AMG 7G-Tronic, E 63 AMG)
2009–2013 Mercedes-Benz W212 (E 200 AMG 7G-Tronic)
2007–2009 Mercedes-Benz W211 (E 230 V6 7G-Tronic)

Mercedes S-Class

2013–2017 Mercedes-Benz W222 (all models except Maybach S 500 and Maybach S 500 4Matic)
2017–2020 Mercedes-Benz W222 (V12 models only)

Non Mercedes-Benz models

Infiniti

2014–2019 Infiniti Q50 (2.0t (M274 DE20 LA)^[12]).
2015–2016 Infiniti Q50 (2.2d (OM651 22 LA)^[13]).
2017–2018 Infiniti Q60 (2.0t (M274 DE20 LA)).

SsangYong Motor

2017–2020 SsangYong Rexton G4 (2.2 e-XDi Euro 6 Turbo-Diesel)
SsangYong Rodius Korando Turismo (in South Korea)
SsangYong Rodius Turismo (in UK)

References

^ ^a ^b "7G-Tronic: Mercedes-Benz presents the world's first seven-speed automatic transmission for passenger cars" (PDF). DaimlerChrysler press release. Archived from the original (PDF) on 2011-07-06. Retrieved 2011-02-22.
^ Borozan, Ion Silviu; Argeșanu, Veronica; Maniu, Inocențiu; Kulcsar, Raul Miklos; Jula, Mihaela (2014). "Metallographic analysis of the 7G-Tronic automatic gearbox housing" (PDF). International Journal of Materials. 1: 119–125. eISSN 2313-0555. Archived (PDF) from the original on 2025-11-07. Retrieved 2025-11-07 – via NAUN.org.
^ 19 July 2010. "Merc plans nine-speed auto'". Autocar.co.uk. Retrieved 2010-07-20.{{cite web}}: CS1 maint: numeric names: authors list (link)
^ ^a ^b ^c "50 years of automatic transmissions from Mercedes-Benz". media.mercedes-benz.com. 2011-04-12. Retrieved 2024-10-29.
^ ^a ^b ^c ^d ^e "Mercedes Benz 722.9 Training Manual" (PDF).
^ "Mercedes Benz 722.9 Workshop Tips and Tricks Manual" (PDF).
^ "Daimler Global Media Site > Mercedes-Benz Cars > AMG". Archived from the original on 2009-08-04. Retrieved 2009-07-20.
^ "The new-generation SLK: More powerful, more economical, more intense | Daimler Global Media Site > Mercedes-Benz Cars > Mercedes-Benz P. Cars > Roadsters > SLK-Class". Archived from the original on 2009-11-10. Retrieved 2009-07-21.
^ "New 7-speed AMG SPEEDSHIFT MCT". Archived from the original on 2009-01-31. Retrieved 2010-07-29.
^ ^a ^b "7G-Tronic Automatic Transmission Catalog (722.9)" (PDF). atra.com. Automatic Transmission Rebuilders Association. Archived from the original (PDF) on 2022-10-13.
^ ^a ^b "Mercedes-Benz Automatic Transmission 722.9 Technical Training Materials - PDF Free Online". Archived from the original on 2019-06-28. Retrieved 2019-06-28.
^ "First view of Mercedes 2.0 turbo in the Infiniti Q50".
^ "Infiniti Q50 2,2d Sport vs. Mercedes-Benz C220 BlueTEC 7G-tronic". 18 October 2014.

External links

7g-Tronic ECU Repair
GermanCarFans
"7G-Tronic: Mercedes-Benz presents the world's first seven-speed automatic transmission for passenger cars" (PDF). DaimlerChrysler press release. Archived from the original (PDF) on 6 July 2011. Retrieved 14 October 2008.
ATT24 GmbH

[4] Differences in gear ratios have a measurable, direct impact on vehicle dynamics, performance, waste emissions as well as fuel mileage

[Forward-5] Forward gears only

[7] 2nd generation of advanced automatic transmissions, at Mercedes-Benz referred to as NAG 2 (New Automatic Gearbox Generation 2 · German: Neue Automatikgetriebe-Generation 2)^[4]

[Torque_Converter-8] Torque converter · German: Wandler or Drehmomentwandler

[14] 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

[6] parallel: using the two degrees of freedom of planetary gearsets
to increase the number of gears

with unchanged number of components

[7] to increase the number of gears

[8] with unchanged number of components

[9] 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

[10] to increase the number of gears

[11] rresponding increase in the number of components is unavoidable

[Progress-15] ^ ^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)

[13] 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

[14] 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

[15] 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)

[16] negative, if the output increases and the input decreases, is perfect

[17] 2 or above is good

[18] 1 or above is acceptable (red)

[19] below this is unsatisfactory (bold)

[16] Direct Predecessor
To reflect the progress of the specific model change

[21] To reflect the progress of the specific model change

[rev2-17] us 2 reverse gears

[rav-20] which 2 gearsets are combined as a compound Ravigneaux gearset

[21] Reference Standard (Benchmark)
In 2008 the 8HP became the new reference standard (benchmark) for automatic transmissions

[25] In 2008 the 8HP became the new reference standard (benchmark) for automatic transmissions

[rev1-22] us 1 reverse gear

[23] Reference Standard (Benchmark) at that time
The 6HP became the new reference standard (benchmark) for automatic transmissions at that time

[28] The 6HP became the new reference standard (benchmark) for automatic transmissions at that time

[24] 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

[30] 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

[31] 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

[32] 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

[33] All transmission variants consist of 7 main components

[34] 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

[35] Turbo-Hydramatic from GM

[36] Cruise-O-Matic from Ford

[37] TorqueFlite from Chrysler

[38] Detroit Gear from BorgWarner for Studebaker

[39] BW-35 from BorgWarner and as T35 from Aisin

[40] 3N 71 from Nissan/Jatco

[41] 3 HP from ZF Friedrichshafen

[42] W3A 040 and W3B 050 from Mercedes-Benz

[25] Revised 14 January 2026
Nomenclature
$S_{n}=$ sun gear: number of teeth

$R_{n}=$ ring gear: number of teeth

$\color {gray}{C_{n}=}$ carrier or planetary gear carrier (not needed)

$s_{n}=$ sun gear: shaft speed

$r_{n}=$ ring gear: shaft speed

$c_{n}=$ carrier or planetary gear carrier: shaft speed
With $n=$ gear is
$i_{n}=$ gear ratio or transmission ratio

$\omega _{1;n}=\omega _{t}=$ shaft speed shaft 1: input (turbine) shaft

$\omega _{2;n}=$ shaft speed shaft 2: output shaft

$T_{1;n}=T_{t}=$ torque shaft 1: input (turbine) shaft

$T_{2;n}=$ torque shaft 2: output shaft

$\mu _{n}=$ torque ratio or torque conversion ratio

$\eta _{n}=$ efficiency

$i_{0}=$ stationary gear ratio

$\eta _{0}=$ (assumed) stationary gear efficiency

[44] $S_{n}=$ sun gear: number of teeth

[45] $R_{n}=$ ring gear: number of teeth

[46] $\color {gray}{C_{n}=}$ carrier or planetary gear carrier (not needed)

[47] $s_{n}=$ sun gear: shaft speed

[48] $r_{n}=$ ring gear: shaft speed

[49] $c_{n}=$ carrier or planetary gear carrier: shaft speed

[50] $i_{n}=$ gear ratio or transmission ratio

[51] $\omega _{1;n}=\omega _{t}=$ shaft speed shaft 1: input (turbine) shaft

[52] $\omega _{2;n}=$ shaft speed shaft 2: output shaft

[53] $T_{1;n}=T_{t}=$ torque shaft 1: input (turbine) shaft

[54] $T_{2;n}=$ torque shaft 2: output shaft

[55] $\mu _{n}=$ torque ratio or torque conversion ratio

[56] $\eta _{n}=$ efficiency

[57] $i_{0}=$ stationary gear ratio

[58] $\eta _{0}=$ (assumed) stationary gear efficiency

[Gear_Ratio-26] ^ ^a ^b ^c ^d ^e ^f ^g ^h ⁱ ^j ^k ^l ^m ⁿ ^o ^p Gear Ratio (Transmission Ratio) $i_{n}$
— Speed Conversion —
The gear ratio $i_{n}$ is the ratio of
input shaft speed $\omega _{1;n}$

to output shaft speed $\omega _{2;n}$

and therefore corresponds to the reciprocal of the shaft speeds
$i_{n}={\frac {1}{\frac {\omega _{2;n}}{\omega _{1;n}}}}={\frac {\omega _{1;n}}{\omega _{2;n}}}={\frac {\omega _{t}}{\omega _{2;n}}}$

[60] The gear ratio $i_{n}$ is the ratio of
input shaft speed $\omega _{1;n}$

to output shaft speed $\omega _{2;n}$

[61] ut shaft speed $\omega _{1;n}$

[62] to output shaft speed $\omega _{2;n}$

[63] therefore corresponds to the reciprocal of the shaft speeds
$i_{n}={\frac {1}{\frac {\omega _{2;n}}{\omega _{1;n}}}}={\frac {\omega _{1;n}}{\omega _{2;n}}}={\frac {\omega _{t}}{\omega _{2;n}}}$

[64] $i_{n}={\frac {1}{\frac {\omega _{2;n}}{\omega _{1;n}}}}={\frac {\omega _{1;n}}{\omega _{2;n}}}={\frac {\omega _{t}}{\omega _{2;n}}}$

[Torque_Ratio-27] ^ ^a ^b ^c ^d ^e ^f ^g ^h ⁱ ^j ^k ^l ^m ⁿ ^o ^p ^q ^r Torque Ratio (Torque Conversion Ratio) $\mu _{n}$
— Torque Conversion —
The torque ratio $\mu _{n}$ is the ratio of
output torque $T_{2;n}$

to input torque $T_{1;n}$

minus efficiency losses

and therefore corresponds (apart from the efficiency losses) to the reciprocal of the shaft speeds too
$\mu _{n}=i_{n}\eta _{n;\eta _{0}}={\frac {\omega _{1;n}\eta _{n;\eta _{0}}}{\omega _{2;n}}}={\frac {T_{2;n}\eta _{n;\eta _{0}}}{T_{1;n}}}$

whereby $\eta _{n;\eta _{0}}$ may vary from gear to gear according to the formulas listed in this table and $0\leq \eta _{n;\eta _{0}}\leq 1$

[66] The torque ratio $\mu _{n}$ is the ratio of
output torque $T_{2;n}$

to input torque $T_{1;n}$

minus efficiency losses

[67] utput torque $T_{2;n}$

[68] to input torque $T_{1;n}$

[69] us efficiency losses

[70] therefore corresponds (apart from the efficiency losses) to the reciprocal of the shaft speeds too
$\mu _{n}=i_{n}\eta _{n;\eta _{0}}={\frac {\omega _{1;n}\eta _{n;\eta _{0}}}{\omega _{2;n}}}={\frac {T_{2;n}\eta _{n;\eta _{0}}}{T_{1;n}}}$

whereby $\eta _{n;\eta _{0}}$ may vary from gear to gear according to the formulas listed in this table and $0\leq \eta _{n;\eta _{0}}\leq 1$

[71] $\mu _{n}=i_{n}\eta _{n;\eta _{0}}={\frac {\omega _{1;n}\eta _{n;\eta _{0}}}{\omega _{2;n}}}={\frac {T_{2;n}\eta _{n;\eta _{0}}}{T_{1;n}}}$

[72] whereby $\eta _{n;\eta _{0}}$ may vary from gear to gear according to the formulas listed in this table and $0\leq \eta _{n;\eta _{0}}\leq 1$

[Efficiency-28] ^ ^a ^b ^c ^d ^e ^f ^g ^h ⁱ ^j ^k ^l ^m Efficiency
The efficiency $\eta _{n}$ is calculated
from the torque ratio

in relation to the gear ratio (transmission ratio)

$\eta _{n}={\frac {\mu _{n}}{i_{n}}}$

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
Corridor for torque ratio and efficiency
in planetary gearsets, the stationary gear ratio $i_{0}$ 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 $\eta _{0}$ specified here are based on assumed efficiencies for the stationary ratio $i_{0}$
of $\eta _{0}=0.9800$ (upper value)

and $\eta _{0}=0.9700$ (lower value)

for both interventions together

The corresponding efficiency
for single-meshing gear pairs is ${\eta _{0}}^{\tfrac {1}{2}}$

at $0.9800^{\tfrac {1}{2}}=0.98995$ (upper value)

and $0.9700^{\tfrac {1}{2}}=0.98489$ (lower value)

[74] The efficiency $\eta _{n}$ is calculated
from the torque ratio

in relation to the gear ratio (transmission ratio)

$\eta _{n}={\frac {\mu _{n}}{i_{n}}}$

[75] rom the torque ratio

[76] relation to the gear ratio (transmission ratio)

[77] $\eta _{n}={\frac {\mu _{n}}{i_{n}}}$

[78] 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

[79] s in the range of 1 % to 1.5 %

[80] r pairs, which are used to reduce noise in passenger cars, are in the upper part of the loss range

[81] spur gear pairs, which are limited to commercial vehicles due to their poorer noise comfort, are in the lower part of the loss range

[82] tary gearsets, the stationary gear ratio $i_{0}$ is formed via the planetary gears and thus by two meshes

[83] r reasons of simplification, the efficiency for both meshes together is commonly specified there

[84] the efficiencies $\eta _{0}$ specified here are based on assumed efficiencies for the stationary ratio $i_{0}$
of $\eta _{0}=0.9800$ (upper value)

and $\eta _{0}=0.9700$ (lower value)

[85] $\eta _{0}=0.9800$ (upper value)

[86] $\eta _{0}=0.9700$ (lower value)

[87] r both interventions together

[88] The corresponding efficiency
for single-meshing gear pairs is ${\eta _{0}}^{\tfrac {1}{2}}$

at $0.9800^{\tfrac {1}{2}}=0.98995$ (upper value)

and $0.9700^{\tfrac {1}{2}}=0.98489$ (lower value)

[89] r single-meshing gear pairs is ${\eta _{0}}^{\tfrac {1}{2}}$

[90] t $0.9800^{\tfrac {1}{2}}=0.98995$ (upper value)

[91] $0.9700^{\tfrac {1}{2}}=0.98489$ (lower value)

[29] Layout
Input and output are on opposite sides

Planetary gearset 2 (the outer Ravigneaux gearset) is on the input (turbine) side

Input (turbine) shafts are R₁ and, if actuated, R₃

Output shaft is C₃

[93] Input and output are on opposite sides

[94] Planetary gearset 2 (the outer Ravigneaux gearset) is on the input (turbine) side

[95] Input (turbine) shafts are R₁ and, if actuated, R₃

[96] Output shaft is C₃

[30] Total Ratio Span (Total Gear Ratio/Total Transmission Ratio) Nominal
${\frac {\omega _{2;n}}{\omega _{2;1}}}={\frac {\frac {1}{\omega _{2;1}}}{\frac {1}{\omega _{2;n}}}}={\frac {\frac {\omega _{t}}{\omega _{2;1}}}{\frac {\omega _{t}}{\omega _{2;n}}}}={\frac {i_{1}}{i_{n}}}$

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

[98] ${\frac {\omega _{2;n}}{\omega _{2;1}}}={\frac {\frac {1}{\omega _{2;1}}}{\frac {1}{\omega _{2;n}}}}={\frac {\frac {\omega _{t}}{\omega _{2;1}}}{\frac {\omega _{t}}{\omega _{2;n}}}}={\frac {i_{1}}{i_{n}}}$

[99] 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

[100] wnspeeding when driving outside the city limits

[101] rease the climbing ability
when driving over mountain passes or off-road

or when towing a trailer

[102] when driving over mountain passes or off-road

[103] r when towing a trailer

[effective-31] Total Ratio Span (Total Gear Ratio/Total Transmission Ratio) Effective
${\frac {min(i_{1};|i_{R}|)}{i_{n}}}$

The span is only effective to the extent that
the reverse gear ratio

matches that of 1st gear

see also Standard R:1

Since reverse gear is usually longer than first gear, the effective span is of central importance for describing the suitability of a transmission. In these cases, the nominal span conveys a misleading picture that is only unproblematic for vehicles with high specific power.
Manufacturers naturally have no interest in specifying the effective span.

Users have not yet formulated the practical benefits that effective span has for them.

Effective span has not yet played a role in research and teaching.
Contrary to its importance, effective span has therefore not been able to establish itself in either theory or practice. It is to be hoped that it will find wider application in the future.

[105] ${\frac {min(i_{1};|i_{R}|)}{i_{n}}}$

[106] The span is only effective to the extent that
the reverse gear ratio

matches that of 1st gear

[107] the reverse gear ratio

[108] tches that of 1st gear

[109] see also Standard R:1

[110] Manufacturers naturally have no interest in specifying the effective span.

[111] Users have not yet formulated the practical benefits that effective span has for them.

[112] Effective span has not yet played a role in research and teaching.

[32] Ratio Span's Center
$(i_{1}i_{n})^{\frac {1}{2}}$

The center indicates the speed level of the transmission

Together with the final drive ratio

it gives the shaft speed level of the vehicle

[114] $(i_{1}i_{n})^{\frac {1}{2}}$

[115] The center indicates the speed level of the transmission

[116] Together with the final drive ratio

[117] t gives the shaft speed level of the vehicle

[33] Average Gear Step
$\left({\frac {i_{1}}{i_{n}}}\right)^{\frac {1}{n-1}}$

With decreasing step width
the gears connect better to each other

shifting comfort increases

[119] $\left({\frac {i_{1}}{i_{n}}}\right)^{\frac {1}{n-1}}$

[120] With decreasing step width
the gears connect better to each other

shifting comfort increases

[121] the gears connect better to each other

[122] shifting comfort increases

[34] Sun 1: sun gear of gearset 1: inner Ravigneaux gearset

[35] Ring 1: ring gear of gearset 1: inner Ravigneaux gearset

[36] Sun 2: sun gear of gearset 2: outer Ravigneaux gearset

[37] Ring 2: ring gear of gearset 2: outer Ravigneaux gearset

[38] Sun 3: sun gear of gearset 3

[39] Ring 3: ring gear of gearset 3

[40] Sun 4: sun gear of gearset 4

[41] Ring 4: ring gear of gearset 4

[50:50-42] 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 3) is always larger

and the upper half of the gear steps (between the large gears; rounded up, here the last 3) 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)

[132] With steadily decreasing gear steps (yellow highlighted line Step)

[133] rticularly large step from 1st to 2nd gear
the lower half of the gear steps (between the small gears; rounded down, here the first 3) is always larger

and the upper half of the gear steps (between the large gears; rounded up, here the last 3) is always smaller

[134] the lower half of the gear steps (between the small gears; rounded down, here the first 3) is always larger

[135] the upper half of the gear steps (between the large gears; rounded up, here the last 3) is always smaller

[136] than the average gear step (cell highlighted yellow two rows above on the far right)

[137] wer half: smaller gear steps are a waste of possible ratios (red bold)

[138] upper half: larger gear steps are unsatisfactory (red bold)

[R3-43] ^ ^a ^b ^c ^d ^e ^f ^g ^h ⁱ ^j In line with the logic for the 2nd reverse gear of the predecessor 5G-Tronic, the extended layout provides this 3rd reverse gear, but it was not used in the transmission that was finally launched on the market

[R:1-44] 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

[141] 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

[142] rment when maneuvering

[143] specially when towing a trailer

[144] torque converter can only partially compensate for this deficiency

[145] Plus 11.11 % minus 10 % compared to 1st gear is good

[146] Plus 25 % minus 20 % is acceptable (red)

[147] Above this is unsatisfactory (bold)

[148] see also Total Ratio Span (Total Gear/Transmission Ratio) Effective

[1:2-45] 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)

[150] With continuously decreasing gear steps (yellow marked line Step)

[151] the largest gear step is the one from 1st to 2nd gear, which
for a good speed connection and

a smooth gear shift

[152] r a good speed connection and

[153] smooth gear shift

[154] ust 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)

[155] A gear ratio of up to 1.6667 : 1 (5 : 3) is good

[156] Up to 1.7500 : 1 (7 : 4) is acceptable (red)

[157] Above is unsatisfactory (bold)

[LS-46] From large to small gears (from right to left)

[Step-47] 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)

[160] 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

[161] increase: Δ Step (first green highlighted line Δ Step) is always greater than 1

[162] As progressive as possible: Δ Step is always greater than the previous step

[163] Not progressively increasing is acceptable (red)

[164] Not increasing is unsatisfactory (bold)

[Speed-48] 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)

[166] Shaft speed differences should
increase: Δ Shaft Speed (second line marked in green Δ (Shaft) Speed) is always greater than the previous one

[167] increase: Δ Shaft Speed (second line marked in green Δ (Shaft) Speed) is always greater than the previous one

[168] 1 difference smaller than the previous one is acceptable (red)

[169] 2 consecutive ones are a waste of possible ratios (bold)

[49] 2nd generation of advanced automatic transmissions, at Mercedes-Benz referred to as NAG 2 (New Automatic Gearbox Generation 2 · German: Neue Automatikgetriebe-Generation 2)^[4]

[50] Permanently coupled elements
C₁/C₂ (the common carrier of the compound Ravigneaux gearset), and R₄

R₃ and C₄

[172] C₁/C₂ (the common carrier of the compound Ravigneaux gearset), and R₄

[173] R₃ and C₄

[51] Blocks S₁ (sun gear of the inner Ravigneaux geaset)

[52] Blocks S₃

[53] Blocks R₂ (ring gear of the outer Ravigneaux gearset)

[54] Blocks R₃ and C₄

[55] Couples S₁ (sun gear of inner Ravigneaux gearset) with R₂ (ring gear of outer Ravigneaux gearset)

[56] Couples R₁ (ring of inner Ravigneaux gearset) with R₃ and C₄

[57] Couples S₃ with S₄

[ordinary-58] Ordinary Noted
For direct determination of the gear ratio

[182] For direct determination of the gear ratio

[elementary-59] 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 the torque ratio and efficiency

[184] Alternative representation for determining the transmission ratio

[185] Contains only operands
With simple fractions of both central gears of a planetary gearset

Or with the value 1

[186] With simple fractions of both central gears of a planetary gearset

[187] Or with the value 1

[188] As a basis
For reliable

And traceable

[189] For reliable

[190] And traceable

[191] Determination of the torque ratio and efficiency

[Eff_Rav-60] Power flow in gearset 2 (the outer Ravigneaux gearset)
the ring gear 1 driven by the turbine acts like an inverted sun gear 1 with the size of sun gear 2

this results in the following power flow:
$R_{1}\Rightarrow Pinions_{1}\Rightarrow Pinions_{2}\Rightarrow R_{2}$

this three meshings are reflected in the exponent of the term for efficiency ${\tfrac {R_{2}}{S_{2}}}{\eta _{0}}^{\tfrac {3}{2}}$ or ${\tfrac {S_{2}}{R_{2}}}{\eta _{0}}^{\tfrac {3}{2}}$

nevertheless, all gear dimensions of gear set 1 can be shortened completely

[193] the ring gear 1 driven by the turbine acts like an inverted sun gear 1 with the size of sun gear 2

[194] this results in the following power flow:
$R_{1}\Rightarrow Pinions_{1}\Rightarrow Pinions_{2}\Rightarrow R_{2}$

this three meshings are reflected in the exponent of the term for efficiency ${\tfrac {R_{2}}{S_{2}}}{\eta _{0}}^{\tfrac {3}{2}}$ or ${\tfrac {S_{2}}{R_{2}}}{\eta _{0}}^{\tfrac {3}{2}}$

nevertheless, all gear dimensions of gear set 1 can be shortened completely

[195] $R_{1}\Rightarrow Pinions_{1}\Rightarrow Pinions_{2}\Rightarrow R_{2}$

[196] this three meshings are reflected in the exponent of the term for efficiency ${\tfrac {R_{2}}{S_{2}}}{\eta _{0}}^{\tfrac {3}{2}}$ or ${\tfrac {S_{2}}{R_{2}}}{\eta _{0}}^{\tfrac {3}{2}}$

[197] vertheless, all gear dimensions of gear set 1 can be shortened completely

[Mercedes-1] "7G-Tronic: Mercedes-Benz presents the world's first seven-speed automatic transmission for passenger cars" (PDF). DaimlerChrysler press release. Archived from the original (PDF) on 2011-07-06. Retrieved 2011-02-22.

[2] Borozan, Ion Silviu; Argeșanu, Veronica; Maniu, Inocențiu; Kulcsar, Raul Miklos; Jula, Mihaela (2014). "Metallographic analysis of the 7G-Tronic automatic gearbox housing" (PDF). International Journal of Materials. 1: 119–125. eISSN 2313-0555. Archived (PDF) from the original on 2025-11-07. Retrieved 2025-11-07 – via NAUN.org.

[3] 19 July 2010. "Merc plans nine-speed auto'". Autocar.co.uk. Retrieved 2010-07-20.{{cite web}}: CS1 maint: numeric names: authors list (link)

[fifty_years-6] "50 years of automatic transmissions from Mercedes-Benz". media.mercedes-benz.com. 2011-04-12. Retrieved 2024-10-29.

[mbmanual1-9] "Mercedes Benz 722.9 Training Manual" (PDF).

[mbmanual2-10] "Mercedes Benz 722.9 Workshop Tips and Tricks Manual" (PDF).

[11] "Daimler Global Media Site > Mercedes-Benz Cars > AMG". Archived from the original on 2009-08-04. Retrieved 2009-07-20.

[12] "The new-generation SLK: More powerful, more economical, more intense | Daimler Global Media Site > Mercedes-Benz Cars > Mercedes-Benz P. Cars > Roadsters > SLK-Class". Archived from the original on 2009-11-10. Retrieved 2009-07-21.

[13] "New 7-speed AMG SPEEDSHIFT MCT". Archived from the original on 2009-01-31. Retrieved 2010-07-29.

[Training_1-18] "7G-Tronic Automatic Transmission Catalog (722.9)" (PDF). atra.com. Automatic Transmission Rebuilders Association. Archived from the original (PDF) on 2022-10-13.

[Training_2-19] "Mercedes-Benz Automatic Transmission 722.9 Technical Training Materials - PDF Free Online". Archived from the original on 2019-06-28. Retrieved 2019-06-28.

[Q50_1-61] "First view of Mercedes 2.0 turbo in the Infiniti Q50".

[Q50_2-62] "Infiniti Q50 2,2d Sport vs. Mercedes-Benz C220 BlueTEC 7G-tronic". 18 October 2014.

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