WO2017063622A1

WO2017063622A1 - Lubricating device for a planetary gear train

Info

Publication number: WO2017063622A1
Application number: PCT/DE2015/200509
Authority: WO
Inventors: Manuel Seubert; Franz Kurth; Ondrej Rybnikár
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2015-10-16
Filing date: 2015-11-17
Publication date: 2017-04-20
Also published as: DE102015222646A1

Abstract

The invention relates to a lubricating device for a planetary gear train, said lubricating device being formed by at least one subarea of a planet carrier of the planetary gear train, at least one lubricating duct in a planetary pin of the planetary gear train, at least one connecting part adjoining the planet carrier, and at least one seal.

Description

Description of the Invention Lubricating device for a planetary drive

FIELD OF THE INVENTION The invention relates to a lubricating device for a planetary drive, wherein the lubricating device is formed by at least one surface portion of a planetary carrier of the planetary drive, at least one lubrication channel in a planetary pinion of the planetary drive, at least one adjacent to the planet carrier connecting member and by at least one seal.

Background of the invention

An example of such a lubricating device is described in DE 10 2009 026 704 A1. A planetary drive is part of a planetary gearbox. The planetary drive is made up of two neighboring planetary gears. The planet carrier of a planetary gear is integrally connected to the ring gear carrier of the other planetary gear. The ring gear is inserted via positive engagement in the ring gear, which is permeable to lubricating oil. The lubricating and cooling oil is to be supplied via a projection of the ring gear the lubrication channels in the planetary pin of the other planetary gear. Between see the ring gear and the ring gear is designed as an O-ring seal and radially clamped. With the seal oil losses are to be avoided via the positive connection of the ring gear with the ring gear.

Description of the invention

The object of the invention is to provide a lubricating device for planetary drives, is optimally distributed by the lubricant to planetary bearings and avoided in the oil losses. The object is solved according to the subject of claim 1. The lubricating device for a planetary drive according to the invention is characterized by

at least one surface section of a one-piece or multi-part planetary carrier, at least one longitudinally or obliquely aligned lubricating channel in a planetary pin,

a first lubricant feed through the planet carrier, wherein the planet carrier or a part of the planet carrier is broken through the formation of the lubricant feedthrough by means of one or more holes,

- At least one connection component, which is adjacent to the planet carrier, and may be a gear, a clutch carrier or any other component, and - at least one seal formed.

The lubricating device has a simple structure, since its structure is formed essentially by the gear components or is integrated in these gear components. On separate components and more of a lubricating device own components, such as the oil trays often used in lubricating devices according to the prior art, can be dispensed with. This contributes to the fact that the planetary drive can be made very compact. The central axis of the planetary drive corresponds to the axis of rotation of the connecting component and a rotatable planet carrier and is the center of the orbit of the planetary gears. The central axis is aligned axially. The planet gears are arranged in radial directions away from the central axis. A surface portion of the planetary carrier and at least a first surface portion of the terminal member together define a hollow and circumferentially extending around the central axis of the planetary gear annulus. The annular space can be designed ringpaltförmig, torus-shaped or a torus similar. It extends around the central axis. In this case, it is not excluded that the annular space is divided into several sections adjacent to one another around the central axis and connected to one another in terms of flow. Alternatively, the annulus is in several circumferentially adjacent and isolated from each other Divided into chambers. The functions of the annulus are the reception, transmission and storage of lubricants. The storage of lubricant has the advantage that when starting the transmission after a long standstill immediately a certain amount of lubricating oil can be supplied to the planetary bearings.

Lubricant passages are for lubricant permeable connections either between a hub and the annulus and / or between the annulus and the

Lubrication channel. For the purposes of the invention, lubricants are all liquid and semi-liquid media suitable for lubrication and cooling, such as lubricating oil and cooling oil.

The planetary carrier and the connection component are at the same time coupled to each other at least via contact of the seal with the planet carrier and the connection component, wherein the seal in a circumferentially extending around the central axis ring-planar contact zone sealingly bears against the planet carrier. It is not excluded that a certain amount of oil leakage arises. However, static seals in the form of O-rings are preferably used, can be avoided by the leak oil in the contact zone.

In applications in which the connection component is pivotable or rotatable relative to the planet carrier about the central axis or otherwise movable relative to the planet carrier, the use of sliding seals is provided. A preferred embodiment of the invention provides that the hub and the planet carrier are formed integrally together, wherein the connection member is seated on the hub. By appropriate design of functionally coordinated surface sections of the hub and the planet carrier, a storage and guide structure can be created, which can be designed as desired. Costly machining can be dispensed with.

One goal is to make planetary gears compact and thus stressing little radial space. The invention relates to planetary drives, in which the connection component is not radially accommodated in a carrier, deviating from the planetary drives described in the chapter "Background of the Invention" and therefore can not be sealed radially outwards or the seal can not be radially clamped As has already been stated, it is axially clamped in. According to one embodiment of the invention, the planet pin has an end face axially against a surface section of the planet carrier, this surface section abutting an axially remote from the contact zone side is formed on the planet carrier. In addition, this surface portion has an opening of the first lubricant feedthrough. As a result, the contact zone is formed partially axially on the rear side of the second surface section.

It is customary, as is also shown in DE 10 2009 026 704 A1, to receive the respective planet pins in an inner cylindrical seat designed as a through hole. For a description of the problem described below, FIG. 6 is used. FIG. 6 shows a detail of a planet carrier 22 with an inner cylindrical seat 23 designed as a through hole for a planet pin 24. Ideally, the end face 24a of the respective planet pin 24 and the peripheral face portion 22a of the planet carrier surrounding the through hole for receiving the respective planet pin 24 lie in a radial plane. The end face 24a can, however, be axially offset by a dimension S1 as a result of position deviations of the planet pin 24 in the range of permissible tolerances with respect to the edge surface section 22a. It is also not excluded that the end face 24a axially protrudes by the dimension S2 over the edge surface portion 22a. In addition, the planet pins 24 are usually end provided with a chamfer 24b or an edge rounding. By this bevel or edge rounding creates an annular groove 25 at the joint gap 26 between the planetary pin 24 and the planet carrier 22. If the outer dimensions of a connection component 10 does not allow it or in other cases in which the designer the diameter D of the seal 18 in a contact zone 15th must put that extends at least partially over the end face 24a and over the joint gap (radially at the height of R and smaller), this is to the detriment. The safe function of seals depends on the quality of the sealing surfaces in the contact zone. The irregularities in the contact zone 15, which are caused by the front or back of the end face 24a of the planet pin 24 and / or by the groove 25, may adversely affect the sealing effect.

The initially described embodiment, according to which the planet pin with an end face bears axially on a surface section in the seat, ensures that the contact zone is not interrupted by such irregularities. The seat of the respective planetary pin in the planet carrier is no longer, as usual, a through hole but a blind hole, the blind hole, however, is interrupted on the bottom side by a lubricant feedthrough. The lubricant feedthrough lies in the radial direction from the central axis below the contact zone of the seal. The lubricating device according to the invention is preferably intended for use in planetary drives of vehicle transmissions such as automatic transmissions in planetary design, in transfer cases or differentials or in all conceivable transmission structures, including those of electric or hybrid vehicles.

Description of the drawings

The invention will be explained in more detail with reference to an embodiment. The illustrations of the figures described below are not to scale.

1 shows a lubricating device of a planetary drive 1 in a longitudinal section along the axially aligned central axis 2 of the planetary drive 1 including a connection component 10. The planetary drive 1 has a planet carrier 3, about the central axis 2 distributed arranged planet pins 4, planetary bearings 5 and planet wheels 6 ,

Figure 2 shows a support plate 3a of the planet carrier 3 with a hub 9 in an overall view. In FIG. 3, the connection component 10 embodied as a gear with external spur toothing is shown in an overall view.

Figure 4 shows a seal 18 formed as an O-ring. Figure 5 is a detailed view, with a view directed axially on the support plate 3a, the seal 18 and a through hole 12b, wherein an end view of a through the seal 18 and the support plate 3a concealed planetary pin 4 is shown in dashed lines. FIG. 1: Each planet pin 4 is supported at a radial distance from the central axis 2 on the left in a carrier plate 3 a of the planet carrier 3 and on the right in a carrier plate 3 b of the planet carrier 3. On each planetary pin 4, a planetary gear 6 is rotatably supported by means of a planetary bearing 5 axially between the support plates 3a and 3b. In each case a planetary pin 4 forms together with a planetary bearing 5 and a planetary gear 6 a building unit. In the view of Figure 1, only a partial view of a planetary gear 6 is visible. The respective planet pin 4 is seated in a blind hole 12 of the support plate 3a. The blind hole 12 is delimited by an inner cylindrical seat 12c for the planetary pin 4 and by a bottom surface portion 12a. The distance of the planet pins 4 from the central axis is the same for all planet pins 4 in the illustrated embodiment. Also conceivable is a planetary drive in which the distances of the planet pins to the central axis are different.

Figures 1 and 5: The planetary pin 4 is designed outside cylindrical throughout. The outer diameter of the planet pins in this case corresponds in nominal size to the diameter of the circular line through which the inner contour of the inner cylindrical seat 12c is outlined. The diameter of the circle of this inner circle 21 accordingly corresponds to the

Diameter of the joint between carrier plate and planet pin.

It is also envisaged that the diameter of the inner cylindrical seat is larger or smaller than the portion of the planetary bolt on which the planetary bearing runs. In this case, the planetary pin is provided with a pin whose diameter is larger or smaller than the diameter of the portion for the planetary bearing. In this case, the section for storage joins a journal of the planetary bolt whose diameter corresponds to the nominal size of the inner diameter of the seat. Figures 1 and 5: The longest radial distance of the inner contour of the inner cylindrical seat is described for all planetary pins 4 by the distance R, which corresponds to the distance of the farthest from the central axis 2 and lying on the inner circle 11 tangent point 19. The definition of the tangent point results from the definition of a tangent. A tangent is known to be a straight line in geometry that touches a given curve at a point. Thereafter, the tangent point 19 is the point where the tangent touches this curve. The curve in this case is the circle of the inner contour 12c.

FIGS. 1 and 2: A through hole 12b extends axially from the surface portion 12a of the planetary carrier 3 through the support plate 3a. The respective planet pin 4 has a longitudinal bore 4a oriented axially parallel to the central axis and closed at the end, which is aligned coaxially with the through-hole 12b. From the respective longitudinal bore 4a transverse bores 4b go in the direction of the planetary bearing 5 from. The support plate 3a is formed integrally with a hub 9. The hub 9 is designed rotationally symmetrical about the central axis 2. On the hub 9 sits a connection member 10. The connection member 10 is in the illustrated embodiment, a spur gear with external teeth. The hub 9 is internally provided with a shaft passage 11 through which a drive shaft, not shown, is guided. Inserted into the hub 9 are through-holes 9a, which extend radially from an annular groove 14 through the wall of the hub 9 to a surface portion 9b of the hub 9 and which open at the surface portion 9b into an annular space 13.

Figure 1: The annular space 13 is on the left side and radially outwardly bounded by a shell-shaped in the terminal member 10 surface portion 10a of the connection member 10, radially inwardly through the surface portion 9b of the hub 9 and the right side by a surface portion 3c. As a result, the annular space 13 extends in the circumferential direction about the central axis 2.

Figures 1 and 5: The connection member 10 is in contact with the support plate 3a. The through-holes 12b is followed radially on the outside by an annular contact zone 15, which is formed by the contact of the gasket 18 clamped between the connection component 10 and the planetary carrier 3 with the carrier plate 3a and which is symbolized by crosses arranged in the illustration according to FIG. The seal 18 abuts on one side of the support plate 3a, which faces away from the surface portions 12a of the blind holes 12 and forms there the sealing contact zone 15 between the connection member 10 and the planet carrier 12. The contact zone 15 is preferably on a circumferentially continuous planar smooth annular surface the support plate 3a is formed. The contact zone 15 in this case runs back on the surface section 12a, so that it either covers the tangent points 19 viewed from the axial direction or, as shown in FIG. 5, radially within an imaginary circle 20 laid around the central axis 2 by the tangent points 19 of each blind hole 12 runs. As a result, the contact zone 15 extends radially at the same height with a portion of the annular surface-shaped end face 4c of the planetary pin.

Figures 1, 2, 3 and 5: The object of the lubricating device is the supply of the planetary bearings 5 with lubricant. The lubricating device consists of the annular groove 14,

Lubricating bushings 16 and 17, from the annular space 13 with the surface portion 3c, from the lubrication channels 7, lubricant feeds 8 from the seal and from the contact zone 15 with the seal 18 and with the gear. Pressurized lubricant or lubricant moved by heavy or centrifugal force is guided out of the annular groove 14 into the annular space 13 through the through holes 9a acting as a lubricant feedthrough 17. The pressure can also be generated by suction or centrifugal force. In this case, the lubricant is conducted from the openings of the lubricant feedthroughs 17, primarily to a guide surface-like surface section 10 a of the gear, to the lubricant feedthroughs 16. The surface portion 10a may be provided with a lubricant litz structure, such as guide ribs. Each of the through holes 12b forms one of the lubricant feedthrough 16. The centrifugal forces guide the lubricant through the lubricant feed structure through the lubricant feedthroughs 16 and into the lubricant channels 7. Each of the longitudinal bores 4 a forms a lubricating channel 7. The lubricant is supplied from the lubricating channels 7 via the lubricant feeds 8, which are designed as transverse bores 4 b, to the respective planetary bearing 5.

Lubricant is collected in the annulus 13. The annular space 13 is in the contact zone 15 radially outwardly, ie, sealed in the flow direction of the lubricant in centrifugal force or gravity. The seal is either a minimal gap between the connection component 10 and the contact zone 15 of the planet carrier 2 or, as shown in FIG. 1, a seal 18.

reference numeral

Planet drive 17 Lubricant feedthrough

Central axis 18 seal

Planet carrier 19 Tangentenpunkta carrier plate 20 imaginary Kreisb carrier plate 21 circular line of Innenkreisesc surface portion 22 planet carrier

Planetary bolt 22 Randflächenabschnitta longitudinal bore 23 seat

b Transverse bore 24 Planetenbolzenc end face 24a end face

Planetary bearing 24b bevel

Planet wheel 25 groove

lubrication channel

lubricant feed

hub

a through hole

b surface section

0 connection component

0a surface section

1 shaft feedthrough

2 blind hole

2a surface section

2b through hole

2c inner contour

3 annulus

4 ring groove

5 contact zone

6 lubricant feedthrough

Claims

claims

1. lubrication device for a planetary drive (1), wherein the lubricating device by

at least one surface section (3c) of a planetary carrier (3) of the planetary drive (1),

- at least one lubrication channel (7) in a planetary pin (4) of the planetary gear (1),

- At least a first lubricant feedthrough (16) by the planet carrier

(3)

- At least one to the planet carrier (3) adjacent terminal member (10) and through

- At least one seal (18) is formed, and wherein

a central axis (2) of the planetary drive (1) corresponds to a rotational axis of the connecting component (10),

- The surface portion (3c) and at least a first surface portion (10a) of the connection component (10) together a hollow and around the central axis (2) of the planetary drive (1) circumferentially extending annular space (13) partially limit,

the first lubricant feedthrough (16) forms a permeable connection between the annular space (13) and the lubricating channel (7),

- The planet carrier (3) and the connection component (10) at least via contact of the seal (18) with the planet carrier (3) and the connection component (10) are coupled to each other at the same time, wherein the seal (18) in a circumferential side to the Central axis (2) extending ring-shaped contact zone

(15) sealingly against the planet carrier (3).

2. Lubricating device according to claim 1, in which the planet pin (4) axially aligned with the central axis (2) on a second surface portion (12 a) of the planet carrier (3), wherein the second surface portion (12 a) an opening of the first lubricant passage (16 ) having.

3. Lubricating device according to claim 2, in which the planet pin (4) abuts the end face on the second surface portion (12a), the second surface portion (12a) on an axially remote from the contact zone (15) side on the planet carrier (3). is trained.

4. Lubricating device according to claim 1 or 3, in which the contact zone (15) and the seal (18) viewed from the central axis (2) from in the radial direction to the annular space (13).

5. Lubricating device according to claim 2 or 3, in which the contact zone (15) is formed partially axially back of the second surface portion (12 a).

6. Lubrication device according to claim 1, in which the seal (18) is a static seal (18).

A lubricating device according to claim 6, in which the seal (18) is an O-ring.

8. lubricating device for a planetary drive (1), wherein the lubricating device

- At least one lubrication channel (7) in a planetary pin (4) of the planetary drive (1),

- At least a first lubricant feedthrough (16) by the planet carrier

(3)

- A hub (9) is formed, and wherein

- The planetary drive (1) has a plurality of planet pins (4),

a central axis (2) of the planetary drive (1) corresponds to an axis of rotation of the connection component (10), the surface section (3c), the first surface section (10a) and a third surface section (9b) of the hub (9) jointly define the annular space (13),

- The hub (9) has a second lubricant passage (17), wherein the second lubricant passage (17) extends radially through the hub (9) and passes into the annular space (13).

9. Lubricating device according to claim 8, with a plurality of circumferentially distributed on the hub second lubricant passages (17) which radially pass through the hub (9) through.

10. A lubricating device according to claim 8, in which the hub (9) and the planetary carrier (3) are integrally formed together, wherein the connecting member (10) on the hub (9) sits and wherein the second surface portion (10 a) between the connecting member (10). 10) and the planet carrier (3).

11. Lubricating device according to claim 8, in which the planet carrier (3) and the hub (9) are integrally formed with each other.

12. Lubricating device according to claim 8, in which at least one circumferentially about the central axis (2) extending and annular contact zone (15) between the connection member (10) and the planet carrier (3) axially between the connection member (10) and the planet carrier (3 ) clamped seal (18) is sealed radially outward.

13. Lubricating device according to claim 12, in which the annular contact zone (15) radially at the same height with a portion of an axially facing end face (4c) of at least one of the planet pins (4).