EP2841797A1

EP2841797A1 - Multi-speed gearbox

Info

Publication number: EP2841797A1
Application number: EP13708836.5A
Authority: EP
Inventors: Stefan Beck; Christian Sibla; Wolfgang Rieger
Original assignee: ZF Friedrichshafen AG
Current assignee: ZF Friedrichshafen AG
Priority date: 2012-04-27
Filing date: 2013-03-13
Publication date: 2015-03-04
Also published as: US20150080168A1; CN104254713B; CN104254713A; DE102012207031A1; WO2013159992A1; DE102012207031B4; US9476482B2

Abstract

The invention relates a four-speed multi-speed gearbox in which a planet carrier (12) of a first planetary gear set (1) and a ring gear (43) of a fourth planetary gear set (4) can be coupled to a housing (72) by means of a first brake (51) or to the drive shaft (70) by means of a first clutch (61), a sun gear (11) of the first planetary gear set (1) can be coupled to the housing (72) by means of a second brake (52), a ring gear (13) of a first planetary gear set (1) and a sun gear (21) of a second planetary gear set (2) can be coupled to the drive shaft (70) by means of a second clutch (62), the drive shaft (70) can be coupled to a ring gear (23) of the second planetary gear set (2) by means of a third clutch (63), a planet carrier (22) of the second planetary gear set (2) is permanently connected to the planet carrier (42) of the fourth planetary gear set (4) and a planet carrier (32) of the third planetary gear set (3) and a sun gear (41) of the fourth planetary gear set (4) are permanently connected to the drive shaft (70). By varying other clutches within the multi-speed gearbox, a set of gearboxes which have similar characteristics are provided.

Description

Mehrstufenqetriebe

The invention relates to a multi-speed planetary gear, in particular for a motor vehicle.

Such multistage transmissions are preferably used as automatic transmissions of motor vehicles, wherein the power flow which is effective in the respective gear ratio within the planetary gear sets is defined by a specific actuation of the shifting elements. The planetary gear sets are usually also connected in an automatic transmission with a slipping action underlying and optionally provided with a lock-up clutch starting element, such as about a hydrodynamic torque converter or a fluid coupling.

From DE 10 2008 000 428 A1 a multi-speed transmission in planetary construction is known, in which four planetary gear sets, and a total of eight rotatable shafts are arranged, one of which represents the drive shaft and another the output shaft of the multi-speed transmission. Furthermore, at least six switching elements are provided in the region of the shafts, by means of whose targeted actuation the power flow within the four planetary gear sets varies and thus different gear ratios between the input and output shafts can be defined. Altogether this means nine forward gears and one reverse gear can be engaged.

The object of the invention is to provide an alternative multi-step transmission, preferably with improved efficiency and sufficiently large and sufficiently uniformly distributed translation series.

The object of the invention is achieved by a multistage transmission according to claim 1. In particular, by a multistage transmission, comprising at least four planetary gear sets, a housing, a drive shaft and an output shaft, wherein a web of a first planetary gear set and a ring gear of a fourth planetary gearset tenradsatzes can be coupled via a first brake with the housing or via a first coupling with the drive shaft,

a sun gear of the first planetary gear set can be coupled to the housing via a second brake,

a ring gear of the first planetary gear set and a sun gear of a second planetary gear set can be coupled via a second clutch to the drive shaft, the drive shaft can be coupled to a ring gear of the second planetary gear set via a third clutch,

a web of the second planetary gear set is permanently connected to a web of the fourth planetary gear set,

a web of a third planetary gear set and a sun gear of the fourth planetary gear set are continuously connected to the drive shaft and one of the following two compounds and one of said compounds are permanently detachable by means of at least one switching element:

Connection of a sun gear of the third planetary gear set with the housing and

Connection of the ring gear of the second planetary gear set with a ring gear of the third planetary gear set.

A planetary gear set is understood to mean, in particular, a wheel set which comprises at least one sun gear, in that one or more planetary gears mesh, a web which determines the axes of the planetary gears and a ring gear in which the planetary gears mesh. Preferably, the ring gear has an internal toothing and the sun gear has an external toothing.

An advantage of the invention may be that the switching elements of the multi-speed transmission, so the gearbox-side brakes and clutches, are easily accessible from the outside. Thus, the actuators such as electric motors, hydraulic valves, hydraulic pumps and the like may be disposed in the vicinity of the switching elements, whereby mechanical and / or hydraulic losses are reduced and a lower energy for the actuation of the switching element may be necessary. Also, less energy may be needed to keep the switching element in its current operating state, ie open or closed, For example, because short lines and the pressure losses are lower. It is also possible to arrange switching elements on the housing and thus at least partially against rotation, whereby seals which connect a stationary line with a rotating line, can be avoided in whole or in part.

Also, the spatial arrangement of the easily accessible switching elements simplifies the replacement of the usual hydraulically actuated multi-plate clutches or - brakes by, for example, electro-mechanical or electro-hydraulically actuated brakes and clutches, which are comparatively easy to use driven. Well achievable switching elements are on the one hand brakes, which rotatably couple a shaft with the housing, but also switching elements on outer shafts of the multi-speed transmission, preferably on input or output shaft, which can be supplied comparatively easy to operate hydraulic fluid.

In addition to this property, the multi-speed transmission also has a good toothing efficiency, only small loads on the components, in particular low Planetenensatz- and switching element moments, low absolute and relative speeds and / or low construction costs. The latter allows the realization of the multi-speed transmission with only low weight and low cost. Finally, the multi-speed transmission also allows a good translation series, so a well usable gradation of the gears.

In general, a preferred embodiment of the multi-speed transmission includes four planetary gear sets, three clutches, three brakes and no fixed housing coupling. An alternative embodiment of the multi-speed transmission generally includes four clutches, two brakes and a solid housing coupling.

By operating two switching elements (brakes and / or clutches), nine forward gears and one reverse gear can be shifted, with three further alternative shift positions being available for the fourth gear. As starting elements, a hydrodynamic torque converter, a hydrodynamic clutch, an additional starting clutch, an integrated starting clutch or brake and / or an additional electric motor can be used.

In principle, an electric motor or another power / power source can be arranged on each shaft. Desweitern can be arranged on each shaft in principle a freewheel to the housing or to another shaft.

Preferably, the multi-speed transmission is realized as a standard drive, but also conceivable is a front-transverse construction.

All switching elements can act frictionally or positively. Preferably, however, the third brake and the fourth clutch are designed as a form-locking brake or clutch, in particular as jaw clutches, which leads to a significantly improved efficiency and thus significant consumption advantages.

It was recognized that the third brake or the fourth clutch must be operated only once when switching from the first to the ninth gear. Therefore, these switching elements are particularly suitable for being designed as a dog clutch. It has thus been further recognized that the advantage of better efficiency outweighs the disadvantage of more difficult handling in these switching elements due to their comparatively rare operation. In particular, it has been recognized that the operation of this switching element can take place at a relatively high gear, whereby the speed difference of the waves can be low and thus is favorable for the operation of a dog clutch.

The geometric position (order) of the individual wheelsets and switching elements is freely selectable, as long as it allows the bindability of the elements. Thus, individual elements can be moved arbitrarily in their position.

Further advantageous variants of the multi-speed transmission result from the subclaims and from the description in conjunction with the figures. These all have the same functional properties as the main system, in particular similar efficiency, similar gradation, etc.

For a better understanding of the invention, this will be explained in more detail with reference to the following figures.

Each shows in a highly schematically simplified representation:

1 shows a first schematically illustrated exemplary variant of a multi-speed transmission according to the invention;

FIG. 2 shows a second schematically illustrated exemplary variant of a multistage transmission according to the invention; FIG.

Fig. 3 is a table showing the closed switching elements for the transmission variant shown in Figure 1 in each gear stage and

Fig. 4 is a table indicating the closed switching elements for the transmission variant shown in Figure 2 in each gear stage.

By way of introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or the same component names, wherein the disclosures contained in the entire description can be mutatis mutandis to the same parts with the same reference numerals or component names. Also, the position information selected in the description, such as top, bottom, side, etc. related to the immediately described and illustrated figure and are to be transferred to a new position analogous to the new situation. Furthermore, individual features or combinations of features from the illustrated and described different embodiments may represent for themselves, inventive or inventive solutions. 1 shows a multistage transmission comprising four planetary gear sets 1, 2, 3, 4, a drive shaft 70, an output shaft 71, six further rotatable shafts 73, 74, 75, 76, 77, 78 six switching elements 51, 52, 53, 61 , 62, 63 thereof three brakes 51, 52, 53 and three clutches 61, 62, 63. The four planetary gear sets 1, 2, 3, 4 are in the order first planetary gear set 1, second planetary gear set 2, third planetary gear set 3, fourth planetary gear set 4th arranged one behind the other. The first planetary gear set 1, the second planetary gear set 2, the third planetary gear set 3 and the fourth planetary gear set 4 are designed as a minus planetary gearset. The planetary gear sets 1, 2, 3, 4, are jointly surrounded by a housing 72. In the variant of the multi-speed transmission of Figure 1 are

a web 12 of a first planetary gear set 1 and a ring gear 43 of a fourth planetary gear set 4 can be coupled via a first brake 51 to the housing 72 or via a first coupling 61 to the drive shaft 70,

a sun gear 1 1 of the first planetary gear set 1 can be coupled to the housing 72 via a second brake 52,

a ring gear 13 of the first planetary gear set 1 and a sun gear 21 of a second planetary gear set 2 can be coupled to the drive shaft 70 via a second clutch 62,

the drive shaft 70 can be coupled to a ring gear 23 of the second planetary gear set 2 via a third clutch 63,

a web 22 of the second planetary gear set 2 is permanently connected to a web 42 of the fourth planetary gear set 4,

a web 32 of a third planetary gear set 3 and a sun gear 41 of the fourth planetary gear set 4 are permanently connected to the drive shaft 70,

the sun gear 31 of the third planetary gear set 3 can be coupled to the housing 72 via a third brake 53 and

the ring gear 23 of the second planetary gear set 2 with the ring gear 33 of the third planetary gear set 3 and shaft 76 is constantly connected.

Fig. 2 shows a multi-stage transmission which is very similar to the multi-speed transmission of Fig. 1 and differs in the following points from the embodiment of Fig. 1:

the sun gear 31 of the third planetary gear set 3 is connected to the housing 72 constantly connected and

the ring gear 23 of the second planetary gear set 2 is permanently connected to the shaft 76 and can be coupled to the ring gear 33 of the third planetary gear set 3 via a fourth clutch 64.

In the case of the multistage transmissions illustrated in FIG. 1, the following gears may be shiftable:

A first gear can be realized by the closed second brake 52, the closed third brake 53 and the closed second clutch 62.

A second gear can be realized by the closed second brake 52, the closed third brake 53 and the closed first clutch 61.

A third gear can be realized by the closed third brake 53, the closed first clutch 61 and the closed second clutch 62.

A fourth gear is through the closed third brake 53, the closed second clutch 62 and the closed third clutch 63 or

by the closed first brake 51, the closed third brake 53 and the closed third clutch 63 or

by the closed second brake 52, the closed third brake 53 and the closed third clutch 63 or

by the closed third brake 53, the closed first clutch 61 and the closed third clutch 63 feasible.

A fifth gear can be realized by the closed first clutch 61, the closed second clutch 62 and the closed third clutch 63.

A sixth gear can be realized by the closed second brake 52, the closed first clutch 61 and the closed third clutch 63.

A seventh gear can be realized by the closed second brake 52, the closed second clutch 62 and the closed third clutch 63.

An eighth gear can be realized by the closed first brake 51, the closed second brake 52 and the closed third clutch 63.

A ninth gear can be realized by the closed first brake 51, the closed second clutch 62 and the closed third clutch 63.

A reverse gear is through the closed first brake 51, the closed third brake 53 and the closed second clutch 62 realized.

The switching elements not mentioned in each case are opened.

This is also shown in the table in Figure 3, which also represents the ratios of the respective gear ratios.

In the case of the multistage transmissions shown in FIG. 2, the following gears can be shiftable:

A first gear can be realized by the closed second brake 52, the closed second clutch 62 and the closed fourth clutch 64.

A second gear can be realized by the closed second brake 52, the closed first clutch 61 and the closed fourth clutch 64.

A third gear can be realized by the closed first clutch 61, the closed second clutch 62 and the closed fourth clutch 64.

A fourth gear is through the closed first clutch 61, the closed third clutch 63 and the closed fourth clutch 64 or

by the closed first brake 51, the closed third clutch 63 and the closed fourth clutch 64 or

by the closed second brake 52, the closed third clutch 63 and the closed fourth clutch 64 or

through the closed second clutch 62, the closed third clutch 63 and the fourth clutch 64 can be realized.

A reverse gear is through the closed first brake 51, the closed second clutch 62 and the closed fourth clutch 64 realized.

The switching elements not mentioned in each case are opened.

This is also shown in the table in Figure 4, which also represents the ratios of the respective gear stages.

Preferably, all wheel sets 1, 2, 3, 4 are designed as Minusradsätze in the multi-speed transmissions shown.

In an advantageous variant, the transmission ratio is:

of the first set of wheels 1 between the sun gear 1 1 and ring gear 13 -3,900 and / or

of the second set of wheels 2 between sun gear 21 and ring gear 23 -2,146 and / or

of the third set of wheels 3 between sun gear 31 and ring gear 33 -1, 634 and / or

of the fourth gear set 4 between sun gear 41 and ring gear 43 -3.045.

In general, instead of a first mentioned connection / coupling to a web 12, 22, 32, 42 of a wheel set 1, 2, 3, 4 and a second mentioned connection / coupling to a ring gear 13, 23, 33, 43 of this wheelset 1, 2nd , 3, 4 the first mentioned connection / coupling to said ring gear 13, 23, 33, 43 of this wheel set 1, 2, 3, 4 and the second said connection / coupling to said web 12, 22, 32, 42 of this wheel set 1, 2, 3, 4 executed, this wheelset 1, 2, 3, 4 instead of a minus wheel as a plus wheel or instead of a plus wheel as a negative wheel is executed. In other words, the connections / couplings to the web 12, 22, 32, 42 and the ring gear 13, 23, 33, 43 of a wheelset 1, 2, 3, 4 exchanged and the direction of rotation between the sun gear 1 1, 21, 31, 41 and ring gear 13, 23, 33, 43 of this wheel 1, 2, 3, 4 vice versa. In the design of the multi-speed transmission is in addition to ensure that the amount of stationary translation of this wheel is increased or decreased by 1, if the switchable ratios between drive 70 and output 71 otherwise remain the same. By said variation of the wheelsets 1, 2, 3, 4 so the connection / coupling between the individual transmission elements can be changed without changing the characteristics of the transmission. This is a variety of structural configurations available, which can simplify the realization of the transmission in an individual case. The mentioned permutation of the connection / coupling is not limited to a wheelset 1, 2, 3, 4, but can also be applied to several wheelsets 1, 2, 3, 4 at the same time.

The embodiments show possible embodiments of a multi-speed transmission according to the invention, it being noted at this point that the invention is not limited to the specifically illustrated embodiments thereof, but rather also various combinations of the individual embodiments are possible with each other and this possibility of variation due to the teaching of technical action representational invention in the skill of those skilled in this technical field. In particular, the possibilities resulting from the combinatorics and the patent claim 1, but not explicitly illustrated in the figures, are also included in the scope of protection. In addition, all conceivable embodiments, which are possible by combinations of individual details of the embodiment variant shown and described, are also included in the scope of protection.

For the sake of order, it should finally be pointed out that for a better understanding of the construction of the multi-speed transmission this is shown schematically in the figures and in reality therefore more components than shown, fewer components than shown or may include other components. In general, the concrete constructive design lies within the scope of expert knowledge.

The task underlying the independent inventive solutions can be taken from the description. First transmission gear set

second gear wheel set

third gear wheel set

fourth gear wheel set

Sun gear of the first gear wheel set Web of the first gear wheel set Ring gear of the first gear wheel set Sun gear of the second gear wheel set Web of the second gear wheel set Ring gear of the second gear wheel Sun wheel of the third gear wheel Set of the third gear wheel set ring gear of third gear wheel set sun gear of the fourth gear wheel set bridge of the fourth gear wheel set ring gear of the fourth gear wheel set first brake

second brake

third brake

first clutch

second clutch

third clutch

fourth clutch

drive

output

casing

, 75, 76, 77, 78 wave

Claims

claims

1 . Multi-speed transmission,

comprising at least four planetary gear sets (1, 2, 3, 4), a housing (72), a drive shaft (70) and an output shaft (71)

a web (12) of a first planetary gear set (1) and a ring gear (43) of a fourth planetary gear set (4) via a first brake (51) to the housing (72) or via a first coupling (61) to the drive shaft (70) can be coupled

a sun gear (1 1) of the first planetary gear set (1) can be coupled to the housing (72) via a second brake (52),

a ring gear (13) of the first planetary gear set (1) and a sun gear (21) of a second planetary gear set (2) can be coupled to the drive shaft (70) via a second clutch (62),

the drive shaft (70) can be coupled to a ring gear (23) of the second planetary gear set (2) via a third clutch (63),

a web (22) of the second planetary gear set (2) is permanently connected to a web (42) of the fourth planetary gear set (4),

a web (32) of a third planetary gear set (3) and a sun gear (41) of the fourth planetary gear set (4) are continuously connected to the output shaft (71) and one of the following two compounds and one of said compounds by means of at least one switching element releasably executed are:

Connection of a sun gear (31) of the third planetary gear set (3) with the housing (72) and

Connection of the ring gear (23) of the second planetary gear set (2) with a ring gear (33) of the third planetary gear set (3).

2. Multi-speed transmission according to claim 1, characterized in that, the sun gear (31) of the third planetary gear set (3) with the housing (72) via a third brake (53) can be coupled and

the ring gear (23) of the second planetary gear set (2) is permanently connected to the ring gear (33) of the third planetary gear set (3) and a sixth shaft (76).

3. Multi-speed transmission according to claim 1, characterized in that, the sun gear (31) of the third planetary gear set (3) with the housing (72) is constantly connected and

the ring gear (23) of the second planetary gear set (2) is permanently connected to a sixth shaft (76) and can be coupled to the ring gear (33) of the third planetary gear set (3) via a fourth clutch (64).

4. Multi-step transmission according to claim 2, characterized in that the following courses are switchable by closing the specified elements:

a first gear through second brake (52), third brake (53) and second clutch (62),

a second gear through second brake (52), third brake (53) and first clutch (61),

a third gear through third brake (53), first clutch (61) and second clutch (62),

a fourth gear by third brake (53), second clutch (62) and third

Coupling (63) or

by first brake (51), third brake (53) and third clutch (63) or by second brake (52), third brake (53) and third clutch (63) or by third brake (53), first clutch (61) and third clutch (63), a fifth gear through first clutch (61), second clutch (62) and third

Coupling (63),

a sixth gear through second brake (52), first clutch (61) and third clutch (63),

a seventh gear by second brake (52), second clutch (62) and third clutch (63),

an eighth gear through first brake (51), second brake (52) and third clutch (63),

a ninth gear by first brake (51), second clutch (62) and third clutch (63) and

a reverse gear through first brake (51), third brake (53) and second clutch (62), wherein the respective elements not mentioned are unactuated or opened.

5. Multi-step transmission according to claim 3, characterized in that the following gears are switchable by closing the specified elements:

a first gear through second brake (52), second clutch (62) and fourth clutch (64),

a second gear through second brake (52), first clutch (61) and fourth clutch (64),

a third gear through first clutch (61), second clutch (62) and fourth clutch (64),

a fourth gear through first clutch (61), third clutch (63) and fourth

Clutch (64) or

by first brake (51), third clutch (63) and fourth clutch (64) or by second brake (52), third clutch (63) and fourth clutch (64) or by second clutch (62), third clutch (63) and fourth clutch (64), a fifth gear through first clutch (61), second clutch (62) and third

Coupling (63),

a seventh gear by second brake (52), second clutch (62) and third clutch (63),

a ninth gear by first brake (51), second clutch (62) and third clutch (63) and

a reverse gear through first brake (51), second clutch (62) and fourth clutch (64),

wherein the respective elements not mentioned are unactuated or opened.

6. Multi-speed transmission according to one of claims 1 to 5, characterized in that all wheelsets (1, 2, 3, 4) are designed as Minusradsätze.

7. Multi-step transmission according to claim 6, characterized in that the transmission ratio :,

of the first gear set (1) between sun gear (1 1) and ring gear (13) -3,900 and / or

of the second wheel set (2) between sun gear (21) and ring gear (23) -2,146 and / or

of the third wheel set (3) between sun gear (31) and ring gear (33) -1, 634 and / or

of the fourth gear set (4) between sun gear (41) and ring gear (43) is -3.045.

8. Multi-speed transmission according to one of claims 1 to 7, characterized in that instead of a first mentioned connection / coupling to a web (12, 22, 32, 42) of a wheel set (1, 2, 3, 4) and a second said connection / Coupling to a ring gear (13, 23, 33, 43) of this wheel set (1, 2, 3, 4), the first-mentioned connection / coupling to said ring gear (13, 23, 33, 43) of this wheel set (1, 2, 3, 4) and the second said connection / coupling to said web (12, 22, 32, 42) of this wheel set (1, 2, 3, 4) is executed, said wheel set (1, 2, 3 , 4) instead of a minus wheel as a plus wheel or instead of a plus wheel as a negative wheel is executed.

9. Multi-step transmission according to one of claims 1 to 8, characterized in that the third brake (53) and fourth clutch (64) are designed as a dog clutch.