DE102011080566A1 - Load-switchable multi-step reduction gear for fragment gear box used in agricultural vehicle, has planetary gear set whose ring gear portion is connected with driven shaft through clutch and spur gear stage portion - Google Patents

Abstract

The multi-step reduction gear has a jackshaft that is arranged parallel to a longitudinal axis of a primary planetary gear set (P1) and a secondary planetary gear set (P2). A drive shaft (1) is connected with a bar region of the secondary planetary gear set. A bar portion of the primary planetary gear set is connected with a driven shaft (2) through a clutch (K4) and a spur gear stage portion (S1). A ring gear portion of the secondary planetary gear set is connected with the driven shaft through a clutch (K5) and a spur gear stage portion (S2).

Description

The present invention relates to a power-shiftable multistage transmission, in particular a splitter gearbox for an agricultural vehicle, according to the preamble of patent claim 1.

Gear for agricultural vehicles usually include a starting clutch, a splitter group, that is serving as a splitter transmission load-switchable input group, a main group or a main gearbox and optionally one, for example, between the input group and the main transmission connected intermediate gear, which is designed as a high-speed gearbox or creep gear ,

Here, the splitter usually has several powershift gears with a small increment, the main group has multiple gears that have a high increment, so that a large number of forward gears is made possible by the combination of a splitter group with a downstream main gear, the Operation of an agricultural vehicle are required.

From the EP 0 495 942 B1 is a multi-stage planetary gear out, which is preferably used as a splitter gear of an agricultural vehicle, which has four arranged in a housing planetary gear sets, a plurality of rotatable shafts and a plurality of switching elements, wherein effected by selective engagement of the switching elements different ratios between the drive shaft and the output shaft of the transmission so that eight gears can be realized.

Furthermore, from the not yet published DE 10 2010 063 496.4 the applicant a planetary gear multi-speed transmission, which is preferably used as a splitter gear of an agricultural vehicle, comprising three arranged in a housing planetary gear sets, a plurality of rotatable shafts and a plurality of switching elements, wherein a third shaft connects a ring gear of a first planetary gear set with a ring gear of a second planetary gear set and can be coupled to the output shaft by means of a first clutch, wherein a fourth shaft which is connected to a sun gear of a first planetary gear set and on the one hand by means of a brake to a housing fixable and on the other via a second clutch with a fifth shaft is connectable provided is, wherein a fifth shaft connected to a sun gear of the second planetary gear set and coupled by means of a third clutch with a sixth shaft, which is in communication with a web of the first planetary gear set and wherein the drive shaft d it is connected to a gear of the second planetary gear set.

The present invention is based on the object, starting from a multi-speed transmission in planetary construction according to the DE 10 2010 063 496.4 the Applicant a power-shiftable multi-speed transmission, in particular a splitter gear for an agricultural vehicle, indicate which viewed axially has a smaller space requirement. In addition, the efficiency should be improved in terms of drag and gearing losses.

This object is achieved by the features of claim 1. Further advantages and advantageous embodiments will become apparent from the dependent claims.

Accordingly, a power-shiftable multi-speed transmission, in particular a splitter gear for an agricultural vehicle is proposed which a drive shaft, two axially successively arranged planetary gear sets, hereinafter referred to as the first and second planetary, a parallel to the longitudinal axis of the planetary gear arranged countershaft, which forms the output shaft of the transmission , two spur gear stages, hereinafter referred to as first and second spur gear stage, and six switching elements comprising a brake and five clutches, the selective engagement of which causes different gear ratios between the input shaft and the output shaft, so that at least eight forward gears are feasible.

The planetary gear sets are preferably designed as negative planetary gear sets. A simple minus planetary gear known to include a sun gear, a ring gear and a ridge on which planet gears are rotatably mounted, each meshing with the sun gear and ring gear. In this way, the ring gear at a fixed web on a sun gear opposite direction of rotation. In contrast, a simple plus planetary gear includes a sun gear, a ring gear and a web on which inner and outer planetary gears are rotatably mounted, wherein all inner planetary gears mesh with the sun gear and all outer planetary gears with the ring gear, each inner planetary gear each having an outer Planet wheel meshes. As a result, the ring gear has the same direction of rotation when the web is held on as the sun gear and there is a positive stationary gear ratio.

According to the invention, the drive shaft is connected to the web of the second planetary gear set, which is releasably connectable via a third coupling with the web of the first planetary gear set, which is releasably connectable via a second clutch with the sun gear of the second planetary gear set, which is detachably connectable via a first clutch to the sun gear of the first planetary gear set which can be coupled via the brake to the housing of the transmission.

Furthermore, the ring gear of the first planetary gear set is connected to the ring gear of the second planetary gear set, wherein the web of the first planetary gear set via a fourth clutch and a first spur gear with the output shaft is releasably connectable and wherein the ring gear of the second planetary gear set via a fifth clutch and a second Spur gear is releasably connected to the output shaft.

The transmission according to the invention is designed in such a way that the space requirement is low in axial view, whereby an arrangement of the transmission as a front-transverse system is simplified.

With the power-shiftable multi-speed transmission according to the invention, the construction cost is considerably reduced by a small number of switching elements. Advantageously, it is possible with the multistage transmission according to the invention to carry out a start with a hydrodynamic converter, an external starting clutch or other suitable external starting elements. It is also conceivable to allow a starting operation with a start-up element integrated in the transmission.

Furthermore, in the multistage transmission according to the invention, a good efficiency in the main drives with respect to the drag and gear losses.

Furthermore, there are low torques in the switching elements and in the planetary gear sets of the multi-speed transmission, whereby the wear is reduced in an advantageous manner. In addition, a correspondingly small dimensioning is made possible by the low torques, whereby the required space and the corresponding costs are reduced. In addition, there are also low speeds at the shafts, the switching elements and the planetary gear sets.

The invention will be explained in more detail below by way of example with reference to the attached figures. These are:

1 a schematic view of a preferred embodiment of a multi-speed transmission according to the invention;

2 a schematic view of another embodiment of a multi-speed transmission according to the invention; and

3 : an exemplary circuit diagram for a multi-step transmission according to 1 and 2 ,

In 1 an inventive power shift multi-speed transmission is shown, with a drive shaft 1 , Two planetary gear sets P1, P2, a parallel to the longitudinal axis of the planetary gear sets P1, P2 arranged countershaft, which the output shaft 2 of the transmission and with a first and a second spur gear S1, S2, which are arranged in a housing G. The planetary gear sets P1, P2 are at the in 1 shown example designed as negative planetary gear sets. According to the invention, at least one planetary gear set can be designed as a positive planetary gear set, if at the same time the web and Hohlradanbindung exchanged and the amount of the stationary gear ratio is increased by 1 compared to the design as a minus planetary gear.

In the embodiment shown, the planetary gear sets are arranged axially in the order P1, P2.

How out 1 can be seen, six switching elements, namely a brake B1 and five clutches K1, K2, K3, K4 and K5 are provided. The spatial arrangement of the switching elements can be arbitrary and is limited only by the dimensions and the external shape. The clutches and the brake of the transmission are preferably designed as Reibschaltelemente or lamellar switching elements, but can also be designed as a form-locking switching elements.

With these switching elements a selective switching of preferably eight forward gears can be realized.

According to the invention in the multi-stage transmission according to 1 provided that the drive shaft 1 is connected to the web of the second planetary gear P2, which is releasably connectable via a third clutch K3 with the web of the first planetary gear set P1, wherein the web of the first planetary gear set P1 via a second clutch K2 with the sun gear of the second planetary gear set P2 is detachably connectable, which can be detachably connected via a first clutch K1 to the sun gear of the first planetary gear set P1 which can be coupled to the housing G of the transmission via the brake B1.

Referring to 1 the ring gear of the first planetary gear P1 is connected to the ring gear of the second planetary gear set P2, wherein the web of the first planetary P1 is connected to a first spur gear ST1 of the first spur gear S1, the second spur gear ST2 via a fourth clutch K4 with the output shaft 2 is detachably connectable, wherein the ring gear of the second Planetary gear P2 is connected to a first spur gear ST3 of the second spur gear S2, whose second spur gear ST4 via a fifth clutch K5 with the output shaft 2 is detachably connectable.

At the in 1 the example shown are the fourth and fifth clutch K4, K5 to the output shaft 2 arranged. Furthermore, the second and the third clutch K2, K3 may have a common outer disk carrier.

In the context of another embodiment of the invention with the same effect, the fourth and fifth clutches K4, K5 are around the drive shaft 1 arranged. This embodiment is the subject of 2 , Here, the web of the first planetary gear set P1 via the fourth clutch K4 with a first spur gear ST1 of the first spur gear S1 is detachably connectable, the second spur gear ST2 with the output shaft 2 connected is. Furthermore, the ring gear of the second planetary gearset P2 via the fifth clutch K5 with a first spur gear ST3 of the second spur gear S2 is releasably connectable, the second spur gear ST4 with the output shaft 2 connected is.

In the context of further embodiments, it is possible, the fourth or the fifth clutch K4, K5 to the drive shaft 1 and the fifth and fourth clutches K5, K4 around the output shaft 2 to arrange the transmission.

The drive shaft 1 of the transmission can be connected to a PTO (PTO), wherein the drive shaft 1 is guided by the designed as a hollow shafts sun gear of the sun gear of the first planetary gear P1 and the sun gear of the second planetary gear set P2.

In 3 is an exemplary circuit diagram of a multi-speed transmission according to 1 and 2 shown. For each gear three switching elements are closed. The shift pattern, the respective ratios of the individual gear ratios i and the therefrom to be determined step jumps or increments φ are taken to the next higher gear example, the value of 3.465 represents the spread of the transmission. As 3 can be seen, a nearly geometric gradation is realized at small increments, whereby the transmission is suitable as a splitter gear.

In the example shown, the values for the stationary gear ratios of the planetary gear sets P1, P2 designed as minus planetary gear sets are -1.800 and -3.500, respectively, with the ratios of the first and second spur gears S1, S2 being 1.555 and 1.000, respectively. Out 3 It can be seen that for the first eight gears in sequential shift mode only one switching element is switched on and one switching element has to be switched off since two adjacent gear stages share two switching elements.

The first forward speed is obtained by closing the brake B1 and the second and fourth clutches K2, K4, the second forward speed by closing the brake B1 and the first and fourth clutches K1, K4, the third forward speed by closing the first, second and fourth clutches K1, K2, K4, the fourth forward gear by closing the first, fourth and fifth clutches K1, K4, K5, the fifth forward gear by closing the second, fourth and fifth clutches K2, K4, K5, the sixth forward speed by closing the brake B1 and the second and fifth clutches K2, K5, the seventh forward speed by closing the brake B1 and the first and fifth clutches K1, K5 and the eighth forward speed results by closing the brake B1 and the third and fifth clutches K3, K5.

The eight forward gears described have an almost geometric increment. Due to the achievable almost geometric increment of the multi-speed transmission, the drive can be reversed to the output, so that the drive shaft 1 as output shaft 2 serves and vice versa. The transmission can be integrated as a splitter transmission in a transmission of an agricultural vehicle, in combination with a group transmission with high increments and optionally with a high-speed gearbox or with a creeper in any geometric order a very high number of courses with high spread of the transmission of the agricultural vehicle to realize.

Referring to 3 can be realized with the transmission according to the invention two additional gears or gear ratios, which result in the circuit diagram underlying stationary gear ratios of the planetary gear sets and ratios of the first and second spur gear, a ratio of each 1.000 and 1.555. These gears are considered optional as they do not result in a nearly geometric grading of the transmission.

The first additional gear, which in the example shown is designed as a direct gear, is obtained by closing the first, second and fifth clutch K1, K2, K5 or by closing the first, third and fifth clutch K1, K3, K5 or by closing the second , third and fifth clutch K2, K3, K5. These variants are in the circuit diagram according to 3 denoted by Z1, M1 or M2.

The second additional gear is obtained by closing the second, third and fourth clutch K2, K3, K4 or by closing the third, fourth and fifth clutch K3, K4, K5 or by closing the first, third and fourth clutch K1, K3, K4. These variants are in the circuit diagram according to 3 denoted M3, M4 and M5, respectively.

The drive motor can be located anywhere on the drive shaft 1 be attached, with the output at any point of the output shaft 2 can be done.

The reverse gears can be realized for example by means of a reversing gear or another, known from the prior art device for reversing the direction of rotation.

According to the invention, even with the same transmission scheme depending on the switching logic different gear jumps, so that an application or vehicle-specific variation is possible.

In principle, an electrical machine or a further drive source can be arranged on each shaft of the transmission according to the invention.

Further, it is possible to provide additional freewheels at any suitable point of the multi-speed transmission, for example, between a shaft and the housing or to connect two shafts optionally.

The starting element of the transmission may be a hydrodynamic torque converter, a hydrodynamic clutch, an additional starting clutch, an integrated starting clutch or starting brake, an electric machine or a power-reversing unit designed according to the prior art.

LIST OF REFERENCE NUMBERS

1

drive shaft

2

output shaft

B1

brake

G

casing

K1

first clutch

K2

second clutch

K3

third clutch

K4

fourth clutch

K5

fifth clutch

P1

first planetary gear set

P2

second planetary gear set

S1

first spur gear

S2

second spur gear

ST1

first spur gear of the first spur gear S1

ST2

second spur gear of the first spur gear S1

ST3

first spur gear of the second spur gear S2

ST4

second spur gear of the second spur gear S2

i

translation

φ

increment

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 0495942 B1 [0004]
• DE 102010063496 [0005, 0006]

Claims (6)

Power-shiftable multistage transmission, in particular splitter gearbox for an agricultural vehicle, comprising a drive shaft ( 1 ), two planetary gear sets (P1, P2), a parallel to the longitudinal axis of the planetary gear sets (P1, P2) arranged countershaft, which the output shaft ( 2 ) of the transmission, a first and a second spur gear (S1, S2), and six switching elements (B1, K1, K2, K3, K4, K5), comprising a brake (B1) and clutches (K1, K2, K3, K4 , K5), whose selective engagement different transmission ratios between the drive shaft ( 1 ) and the output shaft ( 2 ), so that at least eight forward gears are feasible, wherein the drive shaft ( 1 ) is connected to the web of the second planetary gear set (P2), which via a third clutch (K3) to the web of the first planetary gear set (P1) is releasably connectable via a second clutch (K2) with the sun gear of the second planetary gear set (P2 ) is detachably connectable, wherein the sun gear of the second planetary gear set (P2) via a first clutch (K1) with the via the brake (B1) to the housing (G) of the transmission can be coupled detachably sun gear of the first planetary gear set (P1), wherein the ring gear of the first planetary gear set (P1) is connected to the ring gear of the second planetary gear set (P2), the web of the first planetary gear set (P1) being connected via a fourth clutch (K4) and a first spur gear stage (S1) to the output shaft (P1). 2 ) is releasably connectable and wherein the ring gear of the second planetary gear set (P2) via a fifth clutch (K5) and a second spur gear (S2) with the output shaft ( 2 ) is releasably connectable. Multi-speed transmission according to claim 1, characterized in that the planetary gear sets (P1, P2) are designed as negative planetary gear sets. Multi-speed transmission according to claim 1 or 2, characterized in that the fourth and fifth clutch (K4, K5) around the output shaft ( 2 ), wherein the web of the first planetary gear set (P1) with a first spur gear (ST1) of the first spur gear (S1) is connected, the second spur gear (ST2) via the fourth clutch (K4) with the output shaft ( 2 ) is detachably connectable, wherein the ring gear of the second planetary gear set (P2) with a first spur gear (ST3) of the second spur gear (S2) is connected, the second spur gear (ST4) via the fifth clutch (K5) with the output shaft ( 2 ) is releasably connectable. Multi-step transmission according to Claim 1 or 2, characterized in that the fourth and fifth clutches (K4, K5) around the drive shaft ( 1 ), wherein the web of the first planetary gear set (P1) via the fourth clutch (K4) with a first spur gear (ST1) of the first spur gear (S1) is detachably connectable, the second spur gear (ST2) with the output shaft ( 2 ), wherein the ring gear of the second planetary gear set (P2) via the fifth clutch (K5) with a first spur gear (ST3) of the second spur gear (S2) is releasably connectable, the second spur gear (ST4) with the output shaft ( 2 ) connected is. Multi-speed transmission according to claim 1, 2, 3 or 4, characterized in that eight forward gears are realizable, wherein the first forward gear by closing the brake (B1) and the second and fourth clutch (K2, K4), the second Forward gear by closing the brake (B1) and the first and fourth clutch (K1, K4), the third forward gear by closing the first, second and fourth clutch (K1, K2, K4), the fourth forward gear through Closing the first, fourth and fifth clutches (K1, K4, K5), the fifth forward gear by closing the second, fourth and fifth clutches (K2, K4, K5), the sixth forward gear by closing the brake (B1) and the second and fifth clutches (K2, K5), the seventh forward gear by closing the brake (B1) and the first and fifth clutches (K1, K5), and wherein the eighth forward gear is engaged by closing the brake (B1 ) and the third and fifth couplings (K3, K5). Multi-speed transmission according to claim 5, characterized in that two additional gears are feasible, wherein the first additional gear by closing the first, second and fifth clutch (K1, K2, K5) or by closing the first, third and fifth clutch (K1, K3, K5) or by closing the second, third and fifth clutch (K2, K3, K5), and wherein the second additional gear by closing the second, third and fourth clutch (K2, K3, K4) or by closing the third , fourth and fifth clutch (K3, K4, K5) or by closing the first, third and fourth clutches (K1, K3, K4).

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