Gearing for a motor vehicle, and hybrid drive train with same

Patent metadata

Field	Value
Publication number	US-10632835-B2
Application number	US-201615572011-A
Country	US
Kind code	B2
Filing date	Apr 8, 2016
Priority date	May 8, 2015
Publication date	Apr 28, 2020
Grant date	Apr 28, 2020

Abstract

A transmission (G) for a motor vehicle comprising an upstream gear set (VRS), a main gear set (HRS) with a total of four shafts (W 1 , W 2 , W 3 , W 4 ) referred to in order of rotational speeds as first, second, third and fourth shafts, an electric machine (EM), and at least five shift elements (A, B, C, E, F), the selective pairwise closure of which realizes at least eight selectable forward gear ratios (G 1 -G 8 ) between a drive shaft (GW 1 ) and an output shaft (GW 2 ) of the transmission (G). The upstream gear set (VRS) provides a rotational speed at a fifth shaft (W 5 ) increased relative to the rotational speed of the drive shaft (GW 1 ), in a fixed transmission ratio with respect to the drive shaft (GW 1 ). The main gear set (HRS) is a stepped planetary gear set (PS).

First claim

The invention claimed is:

1. A transmission (G) for a motor vehicle, comprising:
a drive shaft (GW 1 );
an output shaft (GW 2 );
an upstream gear set (VRS); and
a main gear set (HRS),
wherein the main gear set has a total of four shafts (W 1 , W 2 , W 3 , W 4 ), the four shafts referred to in order of rotational speeds as a first shaft, a second shaft, a third shaft and a fourth shaft,
wherein the main gear set has first, second, third, fourth and fifth shift elements (A, B, C, E, F), the selective pairwise closure of which realizes at least eight selectable forward gear ratios (G 1 -G 8 ) between the drive shaft (GW 1 ) and the output shaft (GW 2 ) of the transmission (G),
wherein the upstream gear set (VRS) is configured to provide a rotational speed at a fifth shaft (W 5 ) that is increased relative to a rotational speed of the drive shaft (GW 1 ) in a fixed transmission ratio with respect to the drive shaft (GW 1 ),
wherein the fifth shaft (W 5 ) is connectable to the fourth shaft (W 4 ) by closing the first shift element (A),
wherein the fifth shaft (W 5 ) is connectable to the first shaft (W 1 ) by closing the second shift element (B),
wherein the drive shaft (GW 1 ) is connectable to the first shaft (W 1 ) by closing the third shift element (C),
wherein the drive shaft (GW 1 ) is connectable to the second shaft (W 2 ) by closing the fourth shift element (E),
wherein the fourth shaft (W 4 ) is rotationally fixable by closing the fifth shift element (F),
wherein the third shaft (W 3 ) is permanently connected to the output shaft (GW 2 ),
wherein the main gear set (HRS) is a stepped planetary gear set (PS), planet gears (PL) with two effective diameters of different size are rotatably mounted on a carrier (E 22 ) of the stepped planetary gear set (PS), and
wherein the transmission (G) has an electric motor (EM) with a rotationally fixed stator (S) and a rotatable rotor (R), wherein the rotor (R) is permanently rotationally fixedly connected to the fifth shaft (W 5 ).

2. The transmission (G) of claim 1 , wherein:
the stepped planetary gear set (PS) has a first and a second sun gear (E 121 , E 122 ) and a first ring gear (E 321 );
the first sun gear (E 121 ) meshes with the larger effective diameter of the planet gears (FL) and is a constituent part of the first shaft (W 1 );
the second sun gear (E 122 ) meshes with the smaller effective diameter of the planet gears (PL) and is a constituent part of the second shaft (W 2 );
the carrier (E 22 ) is a constituent part of the third shaft (W 3 ); and
the first ring gear (E 321 ) meshes with the larger effective diameter of the planet gears (PL) and is a constituent part of the fourth shaft (W 4 ).

3. The transmission (G) of claim 1 , wherein:
the stepped planetary gear set (PS) has a first sun gear (E 121 ) and a first and a second ring gear (E 321 , E 322 );
the first sun gear (E 121 ) meshes with the smaller effective diameter of the planet gears (PL) and is a constituent part of the first shaft (W 1 );
the carrier (E 22 ) is a constituent part of the second shaft (W 2 );
the first ring gear (E 321 ) meshes with the larger effective diameter of the planet gears (PL) and is a constituent part of the fourth shaft (W 4 ); and
the second ring gear (E 322 ) meshes with the smaller effective diameter of the planet gears (PL) and is a constituent part of the third shaft (W 3 ).

4. The transmission (G) of claim 1 , wherein:
the upstream gear set (VRS) is a planetary gear set (P 1 );
the planetary gear set (P 1 ) has a first element (E 11 ), a second element (E 21 ) and a third element (E 31 );
the first element (E 11 ) is a sun gear of the planetary gear set (P 1 );
the second element (E 21 ) is a carrier of the planetary gear set (P 1 ) when the planetary gear set (P 1 ) is a minus gear set or is a ring gear of the planetary gear set (P 1 ) when the planetary gear set (P 1 ) is a plus gear set;
the third element (E 31 ) is the ring gear of the planetary gear set (P 1 ) when the planetary gear set (P 1 ) is the minus gear set and is the carrier of the planetary gear set (P 1 ) when the planetary gear set (P 1 ) is the plus gear set; and
the first element (E 11 ) is permanently rotationally fixedly immobilized, wherein the second element (E 21 ) is connected to the drive shaft (GW 1 ) and wherein the third element (E 31 ) is a constituent part of the fifth shaft (W 5 ).

5. The transmission (G) of claim 1 , wherein:
a first forward gear ratio (G 1 ) of the at least eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the third shift element (C) and the fifth shift element (F);
a second forward gear ratio (G 2 ) of the at least eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the second shift element (B) and the fifth shift element (F);
a third forward gear ratio (G 3 ) of the at least eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the fourth shift element (E) and the fifth shift element (F);
a fourth forward gear ratio (G 4 ) of the at least eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the second shift element (B) and the fourth shift element (E);
a fifth forward gear ratio (G 5 ) of the at least eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the third shift element (C) and the fourth shift element (E);
a sixth forward gear ratio (G 6 ) of the at least eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the first shift element (A) and the fourth shift element (E);
a seventh forward gear ratio (G 7 ) of the at least eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the first shift element (A) and the third shift element (C); and
an eighth forward gear ratio (G 8 ) of the at least eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the first shift element (A) and the second shift element (B).

6. The transmission (G) of claim 1 , wherein the fifth shift element (F) is a dog-clutch shift element.

7. The transmission (G) of claim 6 , wherein the transmission (G) has a sixth shift element (D), wherein the second shaft (W 2 ) is rotationally fixable by closing the sixth shift element (D), wherein the sixth shift element (D) is open in all forward gear ratios (G 1 -G 8 ).

8. The transmission (G) of claim 7 , wherein a first reverse gear ratio (R 1 ) is realized by closing the third shift element (C) and the sixth shift element (D).

9. The transmission (G) of claim 7 , wherein a second reverse gear ratio (R 2 ) is realized by closing the second shift element (B) and the sixth shift element (D).

10. The transmission (G) of claim 7 , wherein the sixth shift element (D) is a dog-clutch shift element, wherein a parking lock (P) of the transmission (G) is realized by closing the fifth and the sixth shift elements (F, D).

11. The transmission (G) of claim 1 , further comprising a connecting shaft (AN) which is connectable by a seventh shift element (K 0 ) to the drive shaft (GW 1 ).

12. The transmission (G) of claim 11 , further comprising a second electric motor (EM 2 ), a rotor of the second electric motor (EM 2 ) is permanently rotationally fixedly connected to the connecting shaft (AN).

13. A hybrid drivetrain for a motor vehicle comprising the transmission (G) of claim 1 .

Assignees

• Zahnradfabrik Friedrichshafen

Inventors

• Ziemer Peter
• Beck Stefan
• Brehmer Martin
• Horn Matthias
• Kaltenbach Johannes
• King Julian
• Knöpke Bernd
• Moraw Jens
• Münch Eckehard
• Niederbrucker Gerhard
• Pawlakowitsch Juri
• Scharr Stephan
• Warth Viktor
• Wechs Michael
• Griesmeier Uwe
• Kuberczyk Raffael

Classifications

• F16H2200/2007

  with two sets of orbital gears · CPC title

• B60K6/48

  Parallel type · CPC title

• F16H2200/2046

  with six engaging means · CPC title

• B60K6/547 Primary

  the transmission being a stepped gearing · CPC title

• F16H2200/006

  the gear ratios comprising eight forward speeds · CPC title