Planetary transmission

• US 7,278,949 B2
• Filed: 05/18/2004
• Issued: 10/09/2007
• Est. Priority Date: 06/13/2003
• Status: Expired due to Fees

• Current Assignee: ZF Friedrichshafen AG (Zeppelin - Stiftung der Stadt Friedrichshafen)
• Original Assignee: ZF Friedrichshafen AG (Zeppelin - Stiftung der Stadt Friedrichshafen)
• Inventors: Bader, Josef
• Primary Examiner(s): Wright; Dirk
• Application Number:
  US10/557,437
• Publication Number:
  US 20060258502A1
• Time in Patent Office: 1,239 Days
• Field of Search: 475/298, 475/299, 475/300
• US Class Current: 475/298
• CPC Class Codes: F16H 37/046 with an additional planetary gear train, e.g. creep gear, overdrive

Abstract

Proposed is a planetary transmission (8) comprising an internal gear (24), a sun gear (52) and a planet carrier (10), upon which at least one planet gear (20) is supported. The planetary transmission (8) possesses a clutch apparatus with a sliding sleeve (66), which in a first shift-position enables a direct connection between one of the shafts (44) driving the planetary transmission (8) and an output shaft (12) of the planetary transmission (8). In a second shift-position, the connection of the sliding sleeve (66) enables a change in the speed of rotation between the driving shaft (44) and the output shaft (12) of the planetary transmission (8). The planet gear (20) is so supported on the planet carrier (10), that in case of a shifting from a one shift-position into a respective other shift-position, the planet gear (20) on the planet carrier (20) becomes axially slidable.

Claims

1. A planetary transmission (8), comprising an internal gear (24), a sun gear (52) and a planet carrier (10), upon which at least one planet gear (20) is mounted and which possesses a clutch having a sliding sleeve (66), which, in a first shifting position enables a direct connection between one shaft (44) which drives the planetary transmission (8) and an output shaft (12) of the planetary transmission (8), and in a second shifting position, enables a change in the speed of rotation between the main drive shaft (44) and the output shaft (12) of the planetary transmission (8), the planet gear (20) is supported such that the planet carrier (10), when shifting from a one shift-position into an other shift-position, the planet gear (20) on the planet carrier (10) axially slides.

2. The planetary transmission (8) according to claim 1, wherein the planet gear (20) is axially affixed relative to the internal gear (24) and to the sun gear (52), such that are an axial sliding of the planet gear (20) enables a simultaneous axial sliding of the internal gear (24) and the sun gear (52).

3. The planetary transmission (8) according to claim 1, wherein the sliding sleeve (66) has the capability of moving the sun gear (52) axially and therewith the ability to axially slide the planet gear (20) on the planet carrier (10).

4. The planetary transmission (8) according to claim 1, wherein by sliding the planet gear (20) from a one shift-position into an other shift-position, the planet gear (20) travels a smaller sliding path back, than that of the sliding sleeve (66) which moves the planet gear (20).

5. The planetary transmission (8) according to claim 1, wherein the sun gear (52) includes a pressure bolt (48), which coacts with the sliding sleeve (66).

6. The planetary transmission (8) according to claim 1, wherein the sliding sleeve (66) and the sun gear are constructed in one piece.

7. The planetary transmission (8) according to claim 1, wherein both the internal gear (24) as well as the sun gear (52) possess toothed pressure compensators (56, 58, 60, 62) which lie adjacent to the planet gear (20).

8. The planetary transmission (8) according to claim 1, wherein the clutch possesses a neutral position, which lies between the two shift-positions and in which the output shaft (12) of the planetary transmission (8) is not driven.

9. The planetary transmission (8)according to claim 1, wherein the planet gear (20) on the planet carrier (10) is supported by a roller bearing (22).

10. The planetary transmission (8) according to claim 9, wherein the roller bearing (22) includes a multi-row bearing.

11. The planetary transmission (8) according to claim 1, wherein the sun gear (52) and the main drive shaft (44) of the planetary transmission (8) are supported relative to one another.

12. The planetary transmission (8) according to claim 1, wherein a support at the end of the main drive shaft (44) includes a pin (45) with a slotted profile.

13. The planetary transmission (8) according to claim 1, wherein the planetary transmission (8) is presented as an auxiliary gear train, which is designed as a torque transmitting drive string connected to a principal gear drive (6) and by which the output shaft (44) of a principal gear drive (6) forms a driving shaft of the planetary transmission (8).

14. The planetary transmission (8) according to claim 1, wherein the principal gear drive (6) includes two countershafts (40) and one bearing supported main drive shaft (44) which floats between the two countershafts (40), which forms the output shaft of the principal gear drive (6) and which in turn forms the driving shaft of the planetary transmission (8) and which, on an end (46) is supported in the sun gear (52) of the planetary transmission (8).