IP Library › Granted Patent US 10,570,995
Granted Patent B2
US 10,570,995 · App. 15/744,424 · Granted Feb 25, 2020

Transmission for a motor vehicle

Inventors: Stefan Beck (Eriskirch, DE); Michael Wechs (Weißensberg, DE); Martin Brehmer (Tettnang, DE); Johannes Kaltenbach (Friedrichshafen, DE); Eckehard Münch (Bünde, DE); Viktor Warth (Friedrichshafen, DE); Julian King (Rankweil, AT); Jens Moraw (Friedrichshafen, DE); Stephan Scharr (Friedrichshafen, DE); Matthias Horn (Tettnang, DE); Uwe Griesmeier (Markdorf, DE); Peter Ziemer (Tettnang, DE); Juri Pawlakowitsch (Kressbronn, DE); Bernd Knöpke (Salem, DE); Gerhard Niederbrucker (Friedrichshafen, DE); Raffael Kuberczyk (Ravensburg, DE)
Assignee: ZF FRIEDRICHSHAFEN AG
F16H3/663B60K6/365B60K6/48B60K6/547B60K2006/4825F16H2200/006F16H2200/0052F16H2200/0086F16H2200/0091F16H2200/2007F16H2200/2048F16H2200/2064F16H2200/2094F16H2200/2097
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Quick Facts
Patent No.
US 10,570,995
App. No.
15/744,424
Granted
Feb 25, 2020
Kind
B2
Abstract

A transmission (G) for a motor vehicle includes a drive shaft (GW 1 ), an output shaft (GW 2 ), a first and a second planetary gear set (P 1 , P 2 ), and a first, second, third, fourth and fifth shift element ( 04, 13, 14, 26, 36 ). Six forward gear ratios ( 1 - 6 ) between the drive shaft (GW 1 ) and the output shaft (GW 2 ) are engagable through selective pairwise closure of the five shift elements ( 04, 13, 14, 26, 36 ) and rotationally fixed immobilization of the sun gear (E 11 ) of the first planetary gear set (P 1 ).

Claims (42)

1. A transmission (G) for a motor vehicle, comprising:

a drive shaft (GW 1 );

an output shaft (GW 2 );

a first planetary gear set (P 1 ) and a second planetary gear set (P 2 ); and

a first shift element ( 04 ), a second shift element ( 13 ), a third shift element ( 14 ), a fourth shift element ( 26 ) and a fifth shift element ( 36 ),

wherein a carrier (E 21 ) of the first planetary gear set (P 1 ) is permanently connected to a ring gear (E 32 ) of the second planetary gear set (P 2 ),

wherein the output shaft (GW 2 ) is permanently connected to a carrier (E 22 ) of the second planetary gear set (P 2 ),

wherein the carrier (E 21 ) of the first planetary gear set (P 1 ) is rotationally fixable by closing the first shift element ( 04 ),

wherein the drive shaft (GW 1 ) is connectable to a sun gear (E 12 ) of the second planetary gear set (P 2 ) by closing the second shift element ( 13 ),

wherein the drive shaft (GW 1 ) is connectable to the carrier (E 21 ) of the first planetary gear set (P 1 ) by closing the third shift element ( 14 ),

wherein a ring gear (E 31 ) of the first planetary gear set (P 1 ) is connectable to the output shaft (GW 2 ) by closing the fourth shift element ( 26 ),

wherein the ring gear (E 31 ) of the first planetary gear set (P 1 ) is connectable to the sun gear (E 12 ) of the second planetary gear set (P 2 ) by closing the fifth shift element ( 36 ), and

wherein a sun gear (E 11 ) of the first planetary gear set (P 1 ) is either permanently rotationally fixed or switchably rotationally fixable.

2. The transmission (G) of claim 1 , wherein six forward gear ratios ( 1 - 6 ) between the drive shaft (GW 1 ) and the output shaft (GW 2 ) are engagable through selective pairwise closure of the first, second, third, fourth and fifth shift elements ( 04 , 13 , 14 , 26 , 36 ) and rotationally fixed immobilization of the sun gear (E 11 ) of the first planetary gear set (P 1 ), wherein

the first forward gear ratio ( 1 ) is realized by closing the first shift element ( 04 ) and the second shift element ( 13 ),

the second forward gear ratio ( 2 ) is realized by closing the second shift element ( 13 ) and the fourth shift element ( 26 ),

the third forward gear ratio ( 3 ) is realized by closing the second shift element ( 13 ) and the fifth shift element ( 36 ),

the fourth forward gear ratio ( 4 ) is realized by closing the second shift element ( 13 ) and the third shift element ( 14 ),

the fifth forward gear ratio ( 5 ) is realized by closing the third shift element ( 14 ) and the fifth shift element ( 36 ), and

the sixth forward gear ratio ( 6 ) is realized by closing the third shift element ( 14 ) and the fourth shift element ( 26 ).

3. The transmission (G) of claim 1 , wherein the first shift element ( 04 ), the second shift element ( 13 ), or both the first and second shift elements ( 04 , 13 ) is formed as a positively locking shift element.

4. The transmission (G) of claim 1 , wherein an external interface (GW 1 -A) of the drive shaft (GW 1 ) is arranged coaxially with an external interface (GW 2 -A) of the output shaft (GW 2 ), the external interfaces (GW 1 -A, GW 2 -A) of the drive shaft (GW 1 ) and the output shaft (GW 2 ) are arranged at opposite axial ends of the transmission (G), and the second planetary gear set (P 2 ) is positioned axially further from the external interface (GW 1 -A) of the drive shaft (GW 1 ) than the first planetary gear set (P 1 ).

5. The transmission (G) of claim 1 , wherein an external interface (GW 1 -A) of the drive shaft (GW 1 ) is arranged coaxially with an external interface (GW 2 -A) of the output shaft (GW 2 ), the external interfaces (GW 1 -A, GW 2 -A) of the drive shaft (GW 1 ) and the output shaft (GW 2 ) are arranged at a common axial end of the transmission (G), and the second planetary gear set (P 2 ) is positioned axially closer to the external interface (GW 1 -A) of the drive shaft (GW 1 ) than the first planetary gear set (P 1 ).

6. The transmission (G) of claim 1 , further comprising an electric motor (EM) with a rotationally fixed stator (S) and a rotatable rotor (R), wherein the rotor (R) is permanently connected either to the drive shaft (GW 1 ) or to the sun gear (E 12 ) of the second planetary gear set (P 2 ).

7. The transmission (G) of claim 6 , wherein the rotor (R) is permanently connected to the sun gear (E 12 ) of the second planetary gear set (P 2 ), and a superposition operating mode (EDA) is realized by closing the third shift element ( 14 ) and by rotationally fixing the sun gear (E 11 ) of the first planetary gear set (P 1 ).

8. The transmission (G) of claim 1 , further comprising a sixth shift element ( 05 ) and a seventh shift element ( 15 ), wherein the sun gear (E 11 ) of the first planetary gear set (P 1 ) is rotationally fixable by closing the sixth shift element ( 05 ), and the drive shaft (GW 1 ) is connectable to the sun gear (E 11 ) of the first planetary gear set (P 1 ) by closing the seventh shift element ( 15 ).

9. The transmission (G) of claim 8 , wherein the sixth and seventh shift elements ( 05 , 15 ) are positively locking shift elements that are actuatable by a common actuating mechanism.

10. The transmission (G) of claim 8 , wherein a first reverse gear ratio (R 1 ) between drive shaft (GW 1 ) and output shaft (GW 2 ) is realizable by closing the first shift element ( 04 ), the seventh shift element ( 15 ) and the fifth shift element ( 36 ).

11. The transmission (G) of claim 10 , wherein a second reverse gear ratio (R 2 ) is realizable by closing the first shift element ( 04 ), the seventh shift element ( 15 ) and the fourth shift element ( 26 ).

12. The transmission (G) of claim 1 , wherein the first planetary gear set (P 1 ) is a stepped planetary gear set such that the first planetary gear set (P 1 ) has planet gears (PL 1 ) with a smaller effective diameter and a larger effective diameter, the sun gear (E 11 ) of the first planetary gear set (P 1 ) meshes with the smaller effective diameter of the planet pears (PL 1 ), and the ring gear (E 31 ) of the first planetary gear set (P 1 ) meshes with the larger effective diameter of the planet gears (PL 1 ).

13. The transmission (G) of claim 12 , wherein an additional sun gear (E 112 ) of the first planetary gear set (P 1 ) meshes with the larger effective diameter of the planet gears (PL 1 ), and the drive shaft (GW 1 ) is connectable to the additional sun gear (E 112 ) by closing an additional shift element ( 15 b ).

14. The transmission (G) of claim 13 , wherein a reverse gear ratio (R 1 b , R 2 b , R 3 b ) between the drive shaft (GW 1 ) and the output shaft (GW 2 ) is formable by closing the additional shift element ( 15 b ) and the second, fifth or fourth shift element ( 13 , 36 , 26 ).

15. The transmission (G) of claim 12 , wherein an additional ring gear (E 312 ) of the first planetary gear set (P 1 ) meshes with the planet gears (PL 1 ) with the smaller effective diameter, and the output shaft (GW 2 ) is connectable to the additional ring gear (E 312 ) by closing a further additional shift element ( 27 ).

16. The transmission (G) of claim 15 , wherein eight forward gear ratios ( 1 b - 8 b ) between the drive shaft (GW 1 ) and the output shaft (GW 2 ) are engageable through selective pairwise closure of the first through fifth shift elements ( 04 , 13 , 14 , 26 , 36 ) and of the further additional shift element ( 27 ), wherein

the first forward gear ratio ( 1 b ) is realized by closing the first shift element ( 04 ) and the second shift element ( 13 ),

the second forward gear ratio ( 2 b ) is realized by closing the second shift element ( 13 ) and the fourth shift element ( 26 ),

the third forward gear ratio ( 3 b ) is realized by closing the second shift element ( 13 ) and the further additional shift element ( 27 ),

the fourth forward gear ratio ( 4 b ) is realized by closing the second shift element ( 13 ) and the fifth shift element ( 36 ),

the fifth forward gear ratio ( 5 b ) is realized by closing the second shift element ( 13 ) and the third shift element ( 14 ),

the sixth forward gear ratio ( 6 b ) is realized by closing the third shift element ( 14 ) and the fifth shift element ( 36 ),

the seventh forward gear ratio ( 7 b ) is realized by closing the third shift element ( 14 ) and the further additional shift element ( 27 ), and

the eighth forward gear ratio ( 8 b ) is realized by closing the third shift element ( 14 ) and the fourth shift element ( 26 ).

Assignments (1)
ASSIGNMENT OF ASSIGNOR'S INTEREST Recorded Jan 21, 2020
From: BECK, STEFAN; WECHS, MICHAEL; BREHMER, MARTIN; KALTENBACH, JOHANNES; MUNCH, ECKEHARD; WARTH, VIKTOR; KING, JULIAN; MORAW, JENS; SCHARR, STEPHAN; HORN, MATTHIAS; GRIESMEIER, UWE; ZIEMER, PETER; PAWLAKOWITSCH, JURI; KNOEPKE, BERND; NIEDERBRUCKER, GERHARD; KUBERCZYK, RAFFAEL
To: ZF FRIEDRICHSHAFEN AG
Reel/Frame 051562/0676 →
Priority Claims (1)
DE 10 2015 213 664 · Jul 21, 2015 · national
Continuity (1)
Related Publication 20180202520A1 · Jul 19, 2018
Cited By (2)
US 12,404,915 US 12,441,171