DE1555205A1 - Planetary gear change gear especially for motor vehicles - Google Patents

Description

Daimler-Benz share sale

Stuttgart-Untertürkheim irr ο ft ff ² ^ * November 1966

I 0 0 94 Roe Patents / 31

Planetary change gears, in particular for motor vehicles

The invention relates in particular to a planetary gear change transmission For motor vehicles with a 3 forward and 1 reverse gear delivering 1st group of planetary gear sets, which one drive member for all forward and one other drive member for reverse gear, each drive member through a coupling can be connected to the drive motor either or both together.

The invention is based on the object of the transmission of the initially to expand the mentioned genus to a four-speed transmission. This extension should be done in such a way that all 4 courses without group movement can be switched and that also a reverse gear with a stronger reduction is also created at the same time. Further the expansion should be carried out in such a way that it is structurally simple to carry out and possibly the construction of a series of gears makes possible in the manner of a modular system.

This object is achieved according to the invention in the case of the transmissions mentioned at the outset solved in that a 2nd group aJts sun, ring gear and at least one planet gear arranged on a carrier is assigned, the output member of which is connected to the output member of the 1st group rigidly connected, whose 2nd link can be braked and whose 3rd link is connected to another link of the 1st group. In a transmission of the training according to the invention, the 2nd group is only one actuator, namely a brake, is assigned. You can still switch without changing groups. At the same time, there is also a more reduced reverse gear. Finally it is possible for the 2nd group to be activated to leave the construction of the 1st almost unchanged.

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In this way the L & .ger.ii.ltai. ^ Ua; (11 j ! Construction and manufacture of I ¹ eilen and aslu ^ lci it. Ld .; Gears side by side in the manner of a Baukastexi-Iieii.t- v «x-. / Cucii ^ i,

xiei a. -us implementation sfora iiacn of the invention is at d ^ r 1_. Gra ^ aer planet carrier the AbtriQbs ^ lied and the kin _o r ^ n el ε. j abbrejisfcare 2. GIi e tf, v / ob ^ i the sun as a 5 · link LJt aera i'for the forward gears effective drive link of the 1st group is connected. This ^ u ^ leadership fora is especially vo: .. G'-nio ^ t ^; - punlct of a 2sukasten-S ,; Stems from ^ o look advantageous, hi tr h-, -s at the same time the 1st group almost completely unchanged over the ir.-iafcn ".. '<

In a second embodiment according to the invention, the 2nd group uses the gear as the output member urrü the Pl ^ ot'ji ^ r - '. Uerträger as a breakable 2nd member, whereby the sun is al; j 3rd GIior "with the in 2 Corrective supporting member of 1st group Ix, connected. For the sake of clarity, it is warmed up here, but the last mentioned supporting member - apart from the 1st group considered by itself - is about there, ^j supporting member of 1st group Ganges in this group acts.

Within these two embodiments there are a large number of variants using at least partially known characteristics. For example, it is possible according to the invention to form the 1st gear group from zv / ei planetary gear sets, the liingrcd of the 2nd set forming the output and a central gear of the 1st set forming the forward gear drive of this 1st group. For example, the known Simpson theorem is suitable for this. In this Pail both sun gears are rigidly connected to one another in the 1st group and serve as a reverse gear anti-sieve. The ring gear on the 1st set of planetary gears serves as the drive element of the 1st group and the planetary gear carrier of the 2nd set of planetary gears serves as a support element χτη 1st gear (if the 1st group is considered on its own). Another possibility is to use separate sets of planetary gears. Here, the sun gear of the 1st planetary gear set forms the forward gear drive. The two planetary gear carriers on both planetary gear sets are connected to each other and form the support element of the 1st gear (the

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1st group considered on its own), ■■ -

Another courtesy to the realization of the inventive idea lies in the fact that the 1st group of 2 planetary gear sets is ordered, whereby at least one planetary gear belongs to both sets and the Iling gear of the 2nd set the output, the sun of the L set the forward gear - Forms drive of the 1st group. Kan can use a so-called rpine Pt? Vigne? Ux set for this, 1) ο "1 d *? O So on a common planetary wheel carrier at least * - there are two meshing planetary wheels and whereby one of these two planetary planets at the same time also with the! üentralrad of the other planetary gear set cooperates. If you then carry out this last-mentioned single planetary gear with 1 different diameters, you get a combination of a compound planetary set and a lisnrigneeux- * set. By the way, the common planetary is used in both palls. ■ Kirlerträger as a member of the 1st course (the 1st group ■ considered separately) -.

Finally, according to the invention, there is still another embodiment proposed, according to which the 1st group of two planetary gear sets exists, whereby at least one planetary gear belongs to both sets and that the carrier of this common planetary gear is the Abtriob, of the Ivingrad of the wide sat the forward gear drive the 1st group forms. Also in this Pail there are those again Connection of an Itavign «SL-Sat2es with a network planetary set as well as the further possibility of a pure composite system set. As? Support member for the'1. Gang (this group considered in isolation) serves in the first case a Hingrad, in: the latter Pail a Sonnenraä.

In all of the cases described so far, it was always thought of adding the effect of the second group to the first group and also of arranging it spatially behind it. The side facing the downforce is always considered to be the "rear"; i-Ian can, however, significantly simplify the construction of the gearbox if - .. after one.! the 2nd group spatially. before the .1. Group anornnet, v / obei z; wpi same central wheels

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Daim 719074

• both groups are rigidly connected to one another or are formed by a common central wheel. The advantage of this simplification is that - as will be explained in detail later on the basis of the drawings - the number of connecting parts arranged radially between the wheels can be greatly reduced. The execution form with a pure Havigneaux set is particularly advantageous for this simplification. The first and second groups are then formed by a common wheel. A similar picture emerges when using a pure composite planetary set as the 1st group, v / with the sun gears of the 1st and 2nd group then being rigidly connected to one another.

Details of the invention show the embodiments of Drawing namely shows

Pig. 1 to 6 different embodiments - carriers of the Group as output - in the scheme

7 to 12 other embodiments - Hingrad of the 2nd group pe as output - in the scheme,

i ⁿ ig. 13 and 14 further embodiments - 2nd group before the 1st group - again in the scheme.

laughs the pig. 1, the planetary gear change transmission consists of a 1st group 1 and a 2, group II. The 1st group in turn consists of two planetary gear sets 10 and ^ '■. . These two planetary gear sets have a straight sun 12 that can be connected to the drive 13 ^{by a KuPpI 1 JUIg 1C2.} The ring gear Η of the 1st planetary gear set 10 can be connected to the drive I3 by a clutch K1. The carrier 15 of the

1. Planetary gear set 10 is rigid with äem Hingrad 16 des Plaiietenrädersatües 1.1 connected, while the carrier 17 this

2. Planetary gear set 11 can be braked by a 2 brake W.

The second group II consists of a downstream set of planetary gears. Its carrier 10 forms the output and stands

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rigid in connection with the output of 1st group I. That is, e? ~ Is rigid with the connecting cord between the carrier 15 and the ring gear 16 connected. The sun 19 of the 2nd group II stands directly with the univariate 14 »i.e., so» uch ™ it der Coupling K1 in connection. The Ilingrad 20 of the 2nd group II is braked by a brake BI.

'The gearbox is shifted as follows. In all Clutch E1 is engaged in forward gears. First gear is obtained when brake B1 is engaged in addition to this clutch K1. In 2nd gear, the brake B1 just mentioned is then disengaged again and brake B2 is engaged in its place. Pure the 3rd gear, this brake B2 is also disengaged again and a brake B3 is engaged, which engages the common sun gears 12 assigned. For 4th gear this brake B3 is disengaged - so that now no brakes are engaged - and it is In addition to clutch K1, clutch K2 is engaged. As a result, both groups I and II of the planetary gear change transmission are blocked in themselves and run around as a unit. For the reverse gear, clutch K2 is now engaged instead of clutch K1 and in addition to this, the brake B1 is applied.

After Pig. 2, the 2nd group II is structured in the same way. Your carrier 18 in turn forms the output and is in turn in a rigid connection with the ring gear 16. Also the sun gear 19 is connected to the clutch 1, i.e. to the drive for the forward gears.

The 1st group II, however, now consists of two separate planetary gear sets 21 and 22. The sun gear 23 is used for the Planetary gear set .21 as the drive for the forward gears and is therefore connected to clutch K1. The drive the ring gear 24 of the planetary gear set takes over for the reverse gears 21: which is connected to the clutch K2 and also to the probe wheel 25 of the planetary gear set 22 stands. Brake B3 acts on this line. The carriers 26 and are rigidly connected to one another and can be braked by the brake B2.

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The shifting of this gear is carried out in exactly the same way as was already done with Pig above. 1 has been described is.

According to fig. 3, the second group II is again constructed in the same way. Their connection to the first group is also accordingly remained the same.

This first group I is a so-called pure Ravigneaux movement educated. At least two planet gears 29 and 30, which mesh with one another, are arranged on a common carrier 28. A sun 31 engages in planet gear 30, which forms the drive for the forward gears and therefore with clutch K 1 and the sun gear 19 of the second group II is in communication. In the planet gear 29 engages a ring gear 32, which the Forms output of the first group I and is therefore connected to the carrier 18 of the second group II. The planet gear 29 is extended accordingly and meshes with a sun 33 »which forms the drive for reverse gear and with the clutch K 2 is in communication. The brake B 3 still acts on the sun 33.

The shifting of this gear takes place in the same way as it was already done above with Pig. 1 described has been.

After Pig. 4 shows the planetary gear change transmission basically the same structure as according to Pig. 3 * However, it is now in the first group I, the common planet gear 34 formed with two different diameters. In section 35 with the the larger diameter engages the ring gear 36, which forms the drive for the reverse gear and with the clutch K 2 connected and can be braked by the brake B 3. The common one Carrier 28 is now between ring gears 36 and 32 out and braked by the brake B 2.

In this gearbox, too, the shift takes place in the manner described so far Way.

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With the arrangement according to Pig. 5, the second group II is constructed in the manner already described. In contrast, in the first group I, the two sets of planetary gears are interchanged with respect to their position. The larger section 35 of the common sun gear 34- is therefore now at the rear, that is to say on the side facing the output. A single gear 37 meshes with this larger section 35, which forms the drive for the forward gears and is therefore rigidly connected to the clutch K 1 and the sun gear of the second group II. The reverse gear is driven by a sun 38, which is connected to clutch K 2 and can be braked by brake B 3. The second ring gear 39 can be braked by a brake B 2, while the common planet gear carrier AO forms the output of the first group I and is therefore rigidly connected to the carrier 18 of the second group II.

This transmission is shifted in the same way as previously described.

According to FIG. 6, only the sun 38 is in the first group I assigned for the reverse drive to the larger section 35 of the common planetary gear. Another sun 41 is can now be braked by the brake B 2, while the ring gear 37 is again connected to the clutch K 1 for the forward gear drive.

This transmission is also shifted in the same way.

The now following gear of the Pig. 7 to 12 differ basically of the previously described gearboxes with regard to the structure of group II. The structure of the first group I corresponds to the arrangements according to fig. 1 to 6. Likewise accordingly the clutches and brakes are designed and arranged. The shifting of all of these transmissions also takes place again in the same way. It should be noted that the Pig. 7 to 12 an even lower overall, i.e., deliver more indirect first gear. This can be very advantageous in certain applications.

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In the second group II, the ring gear 42 now forms the output. It is therefore in a rigid connection with the output of the first group I. The carrier 43 of the second group II is braked by the brake B 1. It therefore serves as a support member. The sun 4-4 of the second group II is not now more with the drive of group I in connection, but it is rather with the support member of the second gear or - if the first group I is considered by itself - the first course j i.e. in the pail of Figure 7 with the carrier 4-5 des second set of planet gears in the first group I connected. The brake B 2 acts on this connection.

The transmissions according to FIGS. 8 to 12 show the same structure in the second group II as according to FIG. 7> while in terms of the structure of the first group I they are identical to the arrangements according to FIGS.

In the case of the transmission according to FIG. 13, the second group II is arranged at the front and the first group I is arranged at the rear. The latter is as pure composite flange gear set, the carrier 46 of which forms the output and is connected to the single gear 47 of the second group II is in rigid connection. As a drive in all forward gears serves the beef wheel 48, while the one sun 49 den

J
Drive in reverse takes over. These two central gears are connected to the clutches K 1 and E 2 in the manner already described. The second sun *? O of the first group I is rigidly connected to the sun 5Λ of the second group II or it is formed by a central wheel. These two suns can be braked by the brake B 2. The brake B 1 acts on the carrier ^ V of the second group II. The advantage of this type of transmission is that the radial webs engaging between the wheels can be reduced to a minimum. In the arrangement shown, there are only 6 webs 3, for example.

The gear arrangement according to FIG. 14 shows the same advantage. The first group I is now shown as a pure ^ «r / V + aiA / ft

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The common carrier 53 is rigidly connected to the sun 5 ^ of the second group II and can be braked by a brake B 2. Both groups I and II have a common ring gear 55 j. which forms the output. The two suns 56 and. 37 form the drive for the forward and reverse gears and are therefore connected to the clutches K 1 and K 2. This transmission is shifted in the same way as has already been described.

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Claims (4)

15552Ό3 no claims: 1. Planetary gear change transmission, especially for motor vehicles with a three forward and one Reverse gear supplying the first group of planetary gear sets, which are a drive element for all forward and another drive member for the reverse gear, each drive member by a clutch optionally or both can be connected together with the drive motor, characterized in that a second group (II) of the sun, ring gear and at least one planet gear arranged on a carrier is assigned is whose output member is rigidly connected to the output member of the first group, the second member braked and the third member is connected to another member of the first group. 2. planetary gear change transmission according to claim 1, characterized in that that on the second group (II) of the planetary gear carrier (18) the output member and the ring gear (20) the The second link can be braked and the sun (19) as the third link with the drive element effective for the forward gears the first group (I) is in connection. (Figures 1 to 6). 3. planetary gear change transmission according to claim 1, characterized in that that on the second group (II) the ring gear (42) as an output member and the planet gear carrier (43) as Brakeable second member is used and the sun (44) as the third member with the support member effective in the second gear the first group (I) is in connection (Pigur 7 to 12). 4. planetary gear change transmission according to claim 2 or 3 »thereby marked that the first »transmission group (I) from ordered two planetary gear sets and that the ring gear (16) of the second set forms the output and a central gear of the first set forms the forward gear drive of this first group (i) (Pigur 1,2,7 _f 8). 009886 / 03U _by o _mm _ £ _ 4Λ Daim 7190A . Planetary KÄfl ^ v change gear according to claim 2 or 3 characterized in that the first group I consists of two planetary gear sets, at least one Planet gear belongs to both sets and that the ring gear (32) of the second set drives the sun (31) of the second. Set the forward drive of the first Group I forms (Figures 5, 4-, 9 and 10). Planetary gear change transmission according to claim 2 or 3 characterized in that the first group I consists of two planetary gear sets, with at least one planetary gear belongs to both sentences and that the carrier (4-0) of this common planet gear is the output of the ring gear (37) of the second set the forward drive of the first group I forms. (Figure 5 »6, 11 and 12). 7 · planetary gear change gear according to claim 3 and 5 or characterized in that the second group II is spatially arranged in front of the first group I and two of the same Central wheels (55> 51 »50) of both groups rigidly with one another are connected or are formed by a common central wheel. (Figure 15 and 009886 / 03U