DE102008001612A1 - Mobile construction or agricultural machine has power take-off gearbox with hydrostatic drive and mechanical drives located above input shaft - Google Patents

Abstract

A mobile construction or agricultural machine has a drive shaft (3) to an infinitely variable power take-off gear (7) whose input side has a branch stage that distributes power to a hydrostatic stage (19) and a parallel mechanical drive (20). The two drives are coupled to sum the resultant torque values from three linked planetary sets located above the input shaft. The gear has three link shafts for different output shaft (8) speeds. The gear unit also has gear speed selectors.

Description

The The invention relates to a continuously variable power split transmission a mobile work machine, with an input-side branching stage for distributing a voltage applied to an input shaft drive torque on a hydrostatic power branch and parallel to it mechanical power branch, with a coupling gear for summation the torques of the two power branches, which consists of three coaxial over the input shaft arranged and coupled to each other Planetenradsätzen and has three coupling shafts for different output speed ranges, and comprising a plurality of selectively shiftable clutches Switching arrangement for the area-wise transmission of a resulting Output torque on an output shaft.

stepless Power split transmission with a hydrostatic mechanical Performance branching of the aforementioned type have so far been preferred in mobile machines, such as construction machines, especially wheel loaders, Agricultural machinery, such as farm tractors, and forestry machines, with higher drive power for use. It exists the hydrostatic power branch usually from a Hydrostatic unit consisting of a continuously controllable hydrostatic pump and one of these drivable Hydrostatmotor is formed.

The Coupling gear, in which the hydrostatic and the mechanical power branch be merged again, usually includes several together coupled planetary gear sets and has multiple coupling shafts on, at which to realize different driving ranges different output speeds can be tapped. Through a continuous adjustment of the flow rate and the conveying direction of the hydrostatic pump results in a stepless Adjustment of the rotational speeds of the coupling shafts and by a ent speaking constructive design of the linkage and the downstream Switching arrangement a continuous adjustment of the output speeds the driving ranges and a complete speed connection between adjacent driving areas. Thus, in such a Power split transmission the ratio and the output speed of the power split transmission over all driving ranges largely independent of the speed of the input shaft driving drive motor infinitely adjustable.

From the EP 0 408 616 B1 and the DE 42 43 018 A1 In a largely identical embodiment, a corresponding hydrostatic-mechanical power split transmission is known in which the coupling gear consists of three coupled planetary gear sets with a total of three coupling shafts and the switching arrangement of four friction clutches, two friction brakes, and two other coupled planetary gear sets. This known power split transmission has a total of four forward drive ranges and two reverse drive ranges, wherein the direction of rotation of the associated output shaft and thus the direction of travel of the relevant work machine is determined by the switching state of acting on the ring gear of the output side planetary gear friction brake.

From the DE 195 22 833 A1 and the DE 101 28 076 A1 In a largely identical embodiment, another hydrostatic-mechanical power split transmission is known in which the coupling gear also consists of three coupled planetary gear sets with a total of three coupling shafts and the switching arrangement of a total of six friction clutches, a friction brake and another planetary gear. This power split transmission has a total of four forward driving ranges and four equally large reverse drive ranges, the direction of rotation of the associated output shaft and thus the direction of travel of the relevant Arbeitsma machine is determined by the selective switching of a forward drive stage for forward drive and a reversing output stage for reverse drive via an associated friction clutch.

These Although last described power split transmission offer the Possibility of a high output torque and a high driving speed to realize or to increase the overall efficiency to use a relatively small hydrostatic unit. Unfavorable in these known power split transmissions, however, is the relative costly and therefore correspondingly expensive and a large Installation space requiring structure of the switching arrangement, whereby a use in smaller and less powerful machines largely is excluded.

In front In this background, the invention is based on the object stepless power split transmission of the aforementioned To propose way without significant functional limitations simpler and more compact and cheaper can be produced.

The invention is therefore based on a continuously variable power split transmission of a mobile machine, with an input-side branching stage for distributing a voltage applied to an input shaft drive torque to a hydrostatic power branch and a parallel mechanical power branch, with a coupling gear for summing the torques the two power branches, which consists of three coaxial arranged over the input shaft and coupled planetary gear sets and has three coupling shafts for different output speed ranges, and with a plurality of selectively switchable clutches comprehensive switching arrangement for the field-wise transmission of a resultant output torque to an output shaft.

The inventive solution to this problem exists in conjunction with the features of the preamble of the claim 1 in that the switching arrangement two coaxial over the Input shaft arranged intermediate shafts, wherein the first intermediate shaft on the input side via a first clutch with the coupling shaft for low output speeds and over one second clutch with the coupling shaft for middle Output speeds as well as output side over a first Output stage and a first output coupling for forward drive as well as a turning output stage and an output clutch connectable for reversing with the output shaft is, and wherein the second intermediate shaft on the input side rotatably connected to the coupling shaft for high output speeds is and on the output side via a second output stage and a second for forward drive with the output shaft is connectable.

advantageous and expedient refinements and developments the power split transmission according to the invention are the subject matter of claims 2 to 16.

The Thus, the invention is based on a continuously variable power split transmission a mobile work machine that has an input-side branching stage for distributing a voltage applied to an input shaft drive torque on a hydrostatic power branch and parallel to it mechanical power branch, with a coupling gear for summation the torques of the two power branches, which consists of three coaxial over the input shaft arranged and coupled to each other Planetenradsätzen and three coupling shafts for different output speed ranges has, and with a plurality of selectively switchable clutches comprehensive switching arrangement for area-wise transmission a resultant output torque provided on an output shaft is.

In order to save space and weight and manufacturing costs compared to the structure of such, known from the prior art power split transmission space, a simplification of the switching arrangement is provided according to the invention above all. This has therefore a coaxially disposed on the input shaft first intermediate shaft on the input side via a first clutch K ₁ with the coupling shaft for low output speeds and a second clutch K ₂ with the coupling shaft for medium output speeds and the output side via a first output stage S _V1 and a first output coupling for forward drive K _V1 and a turning output stage S _R and an output coupling for reverse K _R with the output shaft is connectable.

Thus, two forward driving ranges and two reverse driving ranges for low and medium driving speeds are realized via the two aforementioned clutches K ₁ , K ₂ and the two output clutches K _V1 , K _R and the associated output stages S _V1 , S _R. Another forward range for high speeds is realized by the fact that the second intermediate shaft input side is rotatably connected to the coupling shaft for high output speeds and the output side via a second output stage S _V2 and a second output coupling for forward drive K _{V2 is} connected to the output shaft.

In favor of a simplified structure of the switching device is thus on a reverse range for high speeds omitted, which is not needed in most machines anyway becomes. Compared to the known power split transmissions are one or two planetary gear sets and at least one Friction clutch or friction brake and the for this Saved components required space.

The first output stage S _V1 and the turning output stage S _R are advantageously arranged axially adjacent to each other, so that the first Abtriebskupp ment for forward drive K _V1 and the output clutch for reverse K _R space saving between the two output stages S _V1 , S _R arranged and with a common Clutch basket can be provided.

The output clutches K _V1 , K _R assigned to the two output stages S _V1 , S _{R of} the first intermediate shaft can optionally be arranged coaxially over the relevant intermediate shaft or the output shaft.

This means in the first case that the first output clutch for forward drive K _V1 and the output clutch for reverse K _R coaxially over the first intermediate shaft are arranged, that a driver element of the two output clutches K _V1 , K _R each rotatably connected to a trained as idler gear input of the associated Output stage S _V1 , S _{R is} in communication, and that the common clutch basket is rotatably connected to the first intermediate shaft.

In the second case is vorgese accordingly hen that the first output clutch for forward drive K _V1 and the output clutch for reverse K _R are arranged coaxially over the output shaft, that a driver element of the two output clutches K _V1 , K _R each rotatably with an idler gear designed as output wheel of the associated output stage S _V1 , S _{R is} in communication, and that the common clutch basket is rotatably connected to the output shaft.

Likewise, the output coupling K _V2 assigned to the second output stage for forward travel S _{V2 of} the second intermediate shaft can optionally be arranged coaxially over the relevant intermediate shaft or the output shaft.

In the first case, this means that the second output clutch for forward travel K _V2 coaxially over the second intermediate shaft is arranged such that a driving element of the second output clutch K _V2 rotation with a designed as a loose wheel input wheel of the second output stage S is connected _V2, and that an associated Clutch basket rotatably connected to the second intermediate shaft.

In this alternative second arrangement is provided corresponding to the second output clutch for forward travel K _V2 coaxially on the output shaft is arranged such that a driving element of the second output clutch K _V2 rotation with a designed as a loose wheel output gear of the second output stage S is connected _V2, and that an associated clutch basket is non-rotatably connected to the output shaft.

In order to avoid formation of the second output clutch K _V2 as a friction clutch, however, it may also be provided that the turning output stage S _R and the second output stage S _V2 are arranged axially adjacent to one another, and that the second output clutch for forward travel K _V2 * together with a further clutch K _R * the turning output stage S _{R is arranged} in a common switching package with a shift sleeve, by means of which the adjacent drive wheels of the second output stage S _V2 and the turning output stage S _R alternately via the output coupling for reverse drive K _{R are} connected to the associated drive shaft.

The output-side power flow in the forward drive range for high speeds and in the reverse drive range is thus in each case via the associated clutch K _V2 *, K _R * of the shift package and the output clutch for reverse K _R. This is possible because the respective driving areas are not directly adjoining each other, ie in a transition between the two driving ranges each of the forward driving range for low and medium speeds, in which the power is transmitted via the first output clutch for forward drive K _V1 , must be passed.

The clutches K _V2 *, K _R * of the common switching package can, as it is known from stepped gearboxes, optionally be designed as unsynchronized jaw clutches or as friction-synchronized jaw clutches.

In order to achieve a gapless connection of the forward driving range for high speeds to the forward driving range for low and medium speeds in the above-described embodiments of the power split transmission according to the invention, with equal size, via the two clutches K ₁ , K ₂ switchable speed ranges of the first and second coupling shaft, the ratio the ratio of the first output stage S _V1 to the ratio of the second output stage S _V2 equal to four (i _V1 / i _V2 = 4).

In a further embodiment of the power split transmission according to the invention, an additional countershaft is provided, which is in drive connection via an associated Endabtriebsstufe S _X with the output shaft, and at least on the second output stage S _V2 'and the associated second output clutch for forward drive K _V2 ' with the second Intermediate shaft is connectable.

By using the additional countershaft results in contrast to the previously described embodiments, the freedom of design, the second output stage S _V2 'either axially output side between the coupling gear and the group of the first output stage S _V1 and the turning output stage S _R ' or axially input side before the coupling gear to arrange.

In both embodiments, the associated output clutch K _V2 'can optionally be arranged coaxially over the second intermediate shaft or the countershaft.

In the first case, this means that the second output clutch for forward travel K _V2 'is arranged coaxially over the second intermediate shaft, that a driver element of the second output clutch K _V2 ' rotatably connected to a formed as idler gear input of the second output stage S _V2 'in combination, and that an associated clutch basket is non-rotatably connected to the second intermediate shaft.

In the second case then results in a similar manner the same way that the second output clutch for forward drive K _V2 'coaxial with the preload is arranged shaft that a driver element of the second output coupling K _V2 'rotatably connected to a trained as idler gear output of the second output stage S _V2 ' is in communication, and that an associated clutch basket is rotatably connected to the countershaft.

In order to achieve a gapless connection of the forward driving range for high speeds to the forward driving range for low and medium speeds even in this embodiment of the power split transmission according to the invention, with the same size, over the two clutches K ₁ , K ₂ switchable speed ranges of the first and second coupling shaft appropriate Ratio of the ratio of the first output stage S _V1 to the product of the ratios of the second output stage S _V2 'and the final output stage S _X equals four (i _V1 / (i _V2 ' * i _X ) = 4).

to Clarification of the invention, the description is a drawing attached with exemplary embodiments. In this shows

1 the schematic structure of a first embodiment of a power split transmission according to the invention,

2 the schematic structure of a second embodiment of a power split transmission according to the invention,

3 the schematic structure of a third embodiment of a power split transmission according to the invention,

4 the schematic structure of a fourth embodiment of a power split transmission according to the invention,

5 the schematic structure of a fifth embodiment of a power split transmission according to the invention, and

6 a speed-speed diagram of one of the power split transmission behind 1 to 5 ,

In a first embodiment according to 1 includes the power split transmission according to the invention 1.1 an input-side branching stage 2 for distributing one to an input shaft 3 applied drive torque to a hydrostatic power branch 4 and a mechanical power branch parallel thereto 5 , a coupling gearbox 6 for summing the torques of the two power branches 4 and 5 , as well as a switching arrangement 7 for the area-wise transmission of a resulting output torque to an output shaft 8th ,

The hydrostatic power branch 4 is from a hydrostatic unit 9 formed from a continuously controllable hydrostatic pump 10 and one of these drivable Hydrostatmotor 11 consists. The mechanical power branch 5 is easy through the input shaft 3 educated. The coupling gear 6 in which the hydrostatic and the mechanical power branch 4 . 5 be merged again, includes three coupled planetary gear sets 12 . 13 . 14 and has three coupling shafts 15 . 16 . 17 for different output speeds.

Because the coupling gear 6 in the same design in the known power split transmissions after the EP 0 408 616 B1 and the DE 195 22 833 A1 is used and described there in detail, its structure and operation at this point can be explained in a condensed form. The hydrostatic engine 11 is via an assigned output stage 18 with the sun gear of the first planetary gear set 12 in drive connection. The input shaft 3 is rotationally fixed with the ring gear of the first planetary gear set 12 connected to the planet carrier of the second planetary gear set 13 is coupled. The planet carrier of the first planetary gear set 12 is rotationally fixed with the ring gear of the second planetary gear set 13 connected to the planet carrier of the third planetary gear set 14 is coupled. The sun gear of the second planetary gear set 13 is rotationally fixed with the sun gear of the third planetary gear set 14 connected.

One with the ring gear of the third planetary gear set 14 connected hollow shaft forms the first coupling shaft 15 , at the one about a continuous adjustment of the Hydrostatic pump 10 infinitely variable output speed of a low speed range can be tapped. An extension of the connecting shaft between the sun gears of the second and third planetary gear set 13 . 14 forms the second coupling shaft 16 , at the one about a continuous adjustment of the Hydrostatic pump 10 infinitely variable output speed of a medium speed range can be tapped. An extension of the connecting shaft between the planet carrier of the first planetary gear set 12 , the ring gear of the second planetary gear set 13 and the planet carrier of the third planetary gear set 14 forms the third coupling shaft 17 , at the one about a continuous adjustment of the Hydrostatic pump 10 infinitely variable output speed of a high speed range can be tapped.

The switching arrangement 7 has two coaxial over the input shaft 3 arranged intermediate waves 19 and 20 on. The first intermediate shaft 19 is the input side via a first clutch K ₁ with the first coupling shaft 15 for low output speeds and a second clutch K ₂ with the second coupling shaft 16 connectable for average output speeds, as well as the output side via a first output stage S _V1 and a first output clutch for forward drive K _V1 and a turning output stage S _R and an output clutch K _R for reverse drive to the output shaft 8th connectable. The second intermediate shaft 20 is input side rotatably with the third coupling shaft 17 connected for high output speeds and the output side via a second output stage S _V2 and a second output coupling for forward drive K _V2 with the output shaft 8th connectable.

In the embodiment of the power split transmission 1.1 to 1 are all output clutches K _V1 , K _V2 , K _R in a so-called in-line arrangement coaxially over the input shaft 3 or over the intermediate waves 19 . 20 arranged. In addition, the first output clutch for forward drive K _V1 and the output clutch for reverse K _R in a common clutch basket 21 summarized.

The first output stage S _V1 consists of a gear pair whose input gear 22 designed as idler gear and rotatably connected to a driver element of the first output clutch for forward drive K _V1 , and its output gear 23 designed as a fixed gear and rotationally fixed to the output shaft 8th connected is.

The turning output stage S _R consists of an input wheel 24 , an idler 25 and a starting wheel 26 comprehensive gear set, with the input gear 24 designed as idler gear and rotatably connected to a driver element of the output clutch for reverse K _R , and the output gear 26 designed as a fixed gear and rotationally fixed to the output shaft 8th connected is. The common clutch basket 21 the output clutches K _V1 , K _R is rotationally fixed with the first intermediate shaft 19 connected.

The second output stage S _V2 consists of a pair of gears whose input gear 27 designed as idler gear and rotatably connected to a driver element of the second output clutch for forward drive K _V2 , and its output gear 28 designed as a fixed gear and rotationally fixed to the output shaft 8th connected is. A clutch basket 29 the second output clutch for forward drive K _V2 is rotatably with the second intermediate shaft 20 connected.

A first driving range for low forward speeds, in which by a corresponding control of the Hydrostatic pump 10 can be approached from a standstill and accelerated to a low speed, is activated by the closing of the first clutch K ₁ and the first output clutch for forward K _V1 . An adjoining second driving range for medium forward speeds, in which by a corresponding control of the Hydrostatic pump 10 can be accelerated from the low vehicle speed to a mean vehicle speed is activated by the closing of the second clutch K ₂ and the keeping closed of the first output clutch K _V1 for forward drive and by the opening of the first clutch K ₁ . A subsequent third driving range for high forward speeds, in which by a corresponding control of the Hydrostatpumpe 10 can be accelerated from the average speed to a high speed, is activated by the closing of the second output clutch for forward drive K _V2 and by the opening of the second clutch K ₂ and the first output clutch for forward drive K _V1 .

Accordingly, a first driving range for low reverse speeds, in which by a corresponding control of the Hydrostatic pump 10 can be moved backwards from standstill and accelerated to a low reverse vehicle speed, activated by the closing of the first clutch K ₁ and the closing of the output clutch for reverse K _R. An adjoining second driving range for medium reverse speeds, in which by a corresponding control of the Hydrostatic pump 10 can be accelerated from the low reverse speed to a medium reverse speed is activated by the closing of the second clutch K ₂ and the closing of the output clutch for reverse K _R and by opening the first clutch K ₁ .

In the power split transmission according to the invention 1.1 There are thus three forward driving ranges and two reverse driving ranges available, between which by an overlapped opening and closing of the respective shift and output clutches K ₁ , K ₂ , K _V1 , K _V2 , K _R can be changed continuously and without interruption of traction, and within the Speed of the output shaft 8th and thus the driving speed of the respective working machine is continuously variable by a continuous adjustment of the height and the conveying direction of the Hydrostatic pump.

This relationship is exemplary for the power split transmission 1.1 to 1 in the diagram of 6 illustrated. In this diagram are for a correspondingly constructed power split transmission 1.1 with n _V1 the speed of the first intermediate shaft 19 , with n _V2 the Speed of the second intermediate shaft 20 and with n _out the speed of the output shaft 8th referred to and represented above the travel speed v of the machine in question. In addition, where R is the entire reverse range in which the output clutch for reverse K _{R is} closed, with V1 the entire lower forward range, in which the first output clutch for forward drive K _{V1 is} closed, and with V2 the upper forward range, in which the second Output coupling for forward travel K _{V2 is} closed, indicated.

As previously explained, however, in the diagram of 6 is not explicitly shown, is in the lower part of the lower forward range V1 (0 km / h to 12 km / h) and the reverse range R (0 km / h to -12 km / h) each closed the first clutch K ₁ , whereas in Upper portion of the lower forward driving range V1 (12 km / h to 24 km / h) and the reverse range R (12 km / h to -24 km / h) in each case the second clutch K _{2 is} closed. As the first coupling shaft 15 and the second coupling shaft 16 or the respective clutches K ₁ , K ₂ associated speed or travel speed ranges are the same size, the ratio of the ratio of the first output stage S _V1 to the translation of the second output stage S _V2 expedient equal to four (i _V1 / i _V2 = 4th ), as a result, a gapless connection of the upper forward drive range V2 is given to the lower forward drive range V1.

A second preferred embodiment of the power split transmission according to the invention 1.2 according to 2 differs from the first embodiment according to 1 only in that all the output clutches K _V1 , K _V2 , K _R now coaxially over the output shaft 8th are arranged. The first output clutch for forward travel K _V1 and the output clutch for reverse K _R are also in a common clutch basket 21 ' summarized.

The first output stage S _V1 consists of a gear pair whose input gear 22 ' now designed as a fixed gear and rotatably with the first intermediate shaft 19 is connected, and its output wheel 23 ' Accordingly formed as idler gear and rotatably connected to a driver element of the first output clutch for forward drive K _V1 .

The turning output stage S _R consists of an input wheel 24 ' , an idler 25 and a starting wheel 26 ' comprehensive gear set, with the input gear 24 ' now designed as a fixed gear and rotatably with the first intermediate shaft 19 connected, and the output gear 26 ' trained accordingly as a loose wheel and rotatably connected to a driver element of the output clutch for reverse K _{R is} connected. The common clutch basket 21 ' The output clutches K _V1 , K _R is therefore rotatably in this gear design with the output shaft 8th connected.

The second output stage S _V2 consists of a pair of gears whose input gear 27 ' now also designed as a fixed gear and rotatably with the second intermediate shaft 20 is connected, and its output wheel 28 ' Accordingly formed as idler gear and rotatably connected to a driver element of the second output clutch for forward drive K _V2 . The clutch basket 29 ' The second output clutch for forward drive K _V2 is therefore also rotationally fixed to the output shaft 8th connected.

The function of the second embodiment of the power split transmission 1.2 to 2 is identical to the first embodiment according to 1 , If it requires special installation conditions or other conditions, the output clutches K _V1 , K _V2 , K _{R can} also in alternating arrangement on the input shaft 3 or on the intermediate shafts 19 . 20 and the output shaft 8th be distributed. Thus, if necessary z. B. the second output clutch K _V2 for forward drive, as in the embodiment according to 1 , coaxial over the input shaft 3 or the second intermediate shaft 20 and the two other output clutches K _V1 , K _R , as in the embodiment according to 2 , coaxial with the output shaft 8th be arranged.

Starting from the second embodiment according to 2 is in a third preferred embodiment of the power split transmission according to the invention 1.3 to 3 the second output clutch for forward drive K _V2 * designed as Reibsynchronisierte clutch and together with a correspondingly formed additional clutch K _R * of the axially adjacent turning output stage S _R in a common switching package 30 combined with a sliding sleeve, by means of which the respective adjacent idler gears 26 ' . 28 ' the turning output stage S _R and the second output stage S _V2 alternately via the output coupling for reverse drive K _R with the output shaft 8th are connectable. When activated reverse range R the power flow thus takes place via the clutch K1 or the clutch K2 on the first intermediate shaft 19 and further on the turning output stage S _R , the additional clutch K _R * and the output clutch for reverse K _R on the output shaft 8th ,

When the upper forward drive range V2 is activated, the power flow takes place from the second intermediate shaft 20 via the second output stage S _V2 , the second output clutch for forward travel K _V2 * and the output clutch for reverse K _R on the off input shaft 8th , By this embodiment, a relatively expensive friction clutch (K _V2 ) is saved and by a comparatively inexpensive and compact switching package 30 replaced with two alternately switchable clutches K _V2 *, K _R *. This is possible in the present case because the second output stage S _V2 and the turning output stage S _R are arranged axially adjacent to one another, and because in driving operation is not directly from the one associated driving range, z. B. the upper forward range V2, in the other associated driving range, z. B. the reverse range R, is changed. Consequently, a timely switching of the switching package 30 before changing the driving range, such. B. the engagement of the clutch K _V2 * before a change from the lower forward driving range V1 in the upper forward driving range V2, easily possible without causing a traction interruption.

In the embodiment according to 3 is the switching package 30 with the two clutches K _V2 *, K _R * coaxial with the output shaft 8th arranged. The switching package 30 However, could also input side, ie coaxially over the input shaft 3 be arranged, provided that the input wheels ( 24 . 27 ) of the second output stage S _V2 and the turning output stage S _R , as in the Ge operating design to 1 , Are designed as idler gears and at least the output clutch K _R for reverse driving coaxially over the input shaft 3 or the first intermediate shaft 19 is arranged.

A fourth embodiment of the power split transmission according to the invention 1.4 to 4 has an additional, short countershaft 31 on, via an associated Endabtriebsstufe S _X with the output shaft 8th' in drive connection stands. The output clutches K _V1 , K _V2 , K _R are, as in the first embodiment after 1 , coaxial over the input shaft 3 or over the associated intermediate waves 19 respectively. 20 arranged. However, the second output stage S _V2 'and the turning output stage S _R ' are now each between the associated intermediate shaft 20 . 19 and the countershaft 31 arranged. Consequently, the turning output stage S _R 'now consists of a gear pair whose input gear 32 formed as idler gear and rotatably connected to a driver element of the output clutch for reverse K _R , and its output gear 33 designed as a fixed wheel and rotationally fixed with the countershaft 31 connected is. The second output stage S _V2 'now consists of an input wheel 34 , an idler 35 and a starting wheel 36 comprehensive gear set, with the input gear 34 designed as idler gear and rotatably connected to a driver element of the second output coupling K _V2 for forward drive, and the output gear 36 designed as a fixed gear and rotationally fixed with the countershaft 31 connected is. The intermediate wheel 35 provides a forward drive for the necessary in this transmission structure reversal direction.

The power flow takes place in this transmission version with activated upper forward range V2 and with activated reverse range on each of the countershaft 31 and the Endabtriebsstufe S _X , which consists of a pair of gears consisting of a rotationally fixed to the countershaft 31 connected fixed wheel 37 and the non-rotatable with the output shaft 8th' connected output wheel 23 the first output stage S _{V1 is} formed. Therefore, for example, the effective translation of the second output stage S _V2 'as a product results from the nominal ratio i _V2 ' of the second output stage S _V2 'and the ratio i _{X of} the final output stage S _X to i _V2'eff = i _v2 ' · i _X , In order to achieve a gapless connection of the upper forward drive range V2 to the lower forward drive range V1 in this transmission design, is at the same size, via the two clutches K1, K2 switchable speed ranges of the first and second coupling shaft 15 . 16 Consequently, the ratio of the ratio of the first output stage S _V1 to the product of the translations of the second output stage S _V2 'and the final output stage S _{X is} advantageously equal to four, ie i _V1 / (i _V2 ' · i _X = 4.

The main advantage of using the additional countershaft 31 exists in the given design possibility, the second output stage S _V2 ', if necessary, also axially input side of the linkage 6 to be able to order. This possibility is in a preferred fifth embodiment of the power split transmission according to the invention 1.5 according to 5 realized. In this transmission design, the second output stage S _V2 'is axially on the input side between the output stage 18 the hydrostatic unit 9 and the first planetary gear set 12 of the linkage 6 and the associated second output clutch for forward travel K _V2 'coaxially over the corresponding axially elongated countershaft 31 ' arranged.

As a result, the input wheel 34 ' the second output stage S _V2 'now formed as a fixed gear and rotation with the axially input side led out second intermediate shaft 20 ' connected. The output wheel 36 ' the second output stage S _V2 'is designed as a loose wheel and rotatably connected to a driver element of the second output clutch for forward drive K _V2 ' whose clutch basket 29 '' rotationally fixed at the input end of the countershaft 31 ' is attached. The operation of the fifth embodiment of the power split transmission according to the invention 1.5 to 5 is identical to that of the fourth embodiment according to 4 ,

1.1

Power split transmission

1.2

Power split transmission

1.3

Power split transmission

1.4

Power split transmission

1.5

Power split transmission

2

branching stage

3

input shaft

4

Hydrostatic power branch

5

mechanical power branch

6

coupling gear

7

switching arrangement

8th

output shaft

8th'

output shaft

9

hydrostatic unit

10

hydrostatic pump

11

hydrostatic

12

first planetary gear

13

second planetary gear

14

third planetary gear

15

First coupling shaft

16

Second coupling shaft

17

third coupling shaft

18

output stage

19

First intermediate shaft

20

Second intermediate shaft

20 '

Second intermediate shaft

21

clutch basket

21

clutch basket

22

input gear, Losrad

22 '

input gear, fixed gear

23

output gear, fixed gear

23 '

output gear, Losrad

24

input gear, Losrad

24 '

input gear, fixed gear

25

idler

26

output gear, fixed gear

26 '

output gear, Losrad

27

input gear, Losrad

27 '

input gear, fixed gear

28

output gear, fixed gear

28 '

output gear, Losrad

29

clutch basket

29 '

clutch basket

29 ''

clutch basket

30

switching package

31

Countershaft

31 '

Countershaft

32

input gear, Losrad

33

output gear, fixed gear

34

input gear, Losrad

34 '

input gear, fixed gear

35

idler

36

output gear, fixed gear

36 '

output gear, Losrad

37

fixed gear

i _V1

Translation of S _V1

i _V2

Translation of S _V2

i _V2 '

Nominal translation of S _V2 '

i _V2'eff

effective translation of S _V2 '

i _X

Translation of S _X

K _R

output coupling for reversing

K _R *

Clutch (from S _R )

K _V1

First Output coupling for forward drive

K _V2

Second Output coupling for forward drive

K _V2 '

Second Output coupling for forward drive

K _V2 *

Clutch of (S _V2 ), second output clutch

K ₁

First clutch

K ₂

Second clutch

n

rotation speed

n _OFF

Speed of output shaft ( 8th )

n _V1

Speed of first intermediate shaft ( 19 )

n _V2

Speed of second intermediate shaft ( 20 )

R

Reverse range

S _R

Turning output stage

S _R '

Turning output stage

S _V1

First output stage

S _V2

Second output stage

S _V2

Second output stage

S _X

Endabtriebsstufe

V

driving speed

V1

lower Forward Range

V2

Oberer Forward Range

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - EP 0408616 B1 [0004, 0041]
• - DE 4243018 A1 [0004]
• DE 19522833 A1 [0005, 0041]
• - DE 10128076 A1 [0005]

Claims (16)

Continuously variable power split transmission of a mobile work machine, with an input-side branching stage ( 2 ) for distributing one to an input shaft ( 3 ) adjacent drive torque to a hydrostatic power branch ( 4 ) and a parallel mechanical power branch ( 5 ), with a coupling gear ( 6 ) for summing the torques of the two power branches ( 4 . 5 ), which consists of three planetary gear sets arranged coaxially over the input shaft and coupled together ( 12 . 13 . 14 ) and three coupling waves ( 15 . 16 . 17 ) for different output speed ranges, and with a plurality of selectively switchable clutches (K ₁ , K ₂ , K _V1 , K _V2 , K _R ) comprehensive switching arrangement ( 7 ) for the area-wise transmission of a resulting output torque to an output shaft ( 8th ), characterized in that the switching arrangement ( 7 ) two coaxially over the input shaft ( 3 ) intermediate shafts ( 19 . 20 ), wherein the first intermediate wave ( 19 ) on the input side via a first clutch (K ₁ ) with the coupling shaft for low output speeds ( 15 ) and via a second clutch (K ₂ ) with the coupling shaft ( 16 ) for medium output speeds as well as on the output side via a first output stage (S _V1 ) and a first output clutch for forward drive (K _V1 ) as well as a turning output stage (S _R ) and a driven clutch for reverse drive (K _R ) with the output shaft ( 8th ) is connectable, and wherein the second intermediate shaft ( 20 ) on the input side rotatably with the coupling shaft ( 17 ) is connected for high output speeds and the output side via a second output stage (S _V2 ) and a second output clutch for forward drive (K _V2 ) with the output shaft ( 8th ) is connectable. Power split transmission according to claim 1, characterized in that the first output stage (S _V1 ) and the turning output stage (S _R ) are arranged axially adjacent to each other, and that the first output clutch for forward travel (K _V1 ) and the output clutch for reverse (K _R ) between the two output stages (S _V1 , S _R ) are arranged and a common clutch basket ( 21 ) exhibit. Power split transmission according to claim 2, characterized in that the first output clutch for forward drive (K _V1 ) and the output clutch for reverse drive (K _R ) coaxially over the first intermediate shaft ( 19 ) are arranged such that a driver element of the two output clutches (K _V1 , K _R ) each rotatably with an input gear designed as a loose wheel ( 22 . 24 ) of the associated output stage (S _V1 , S _R ) is in communication, and that the common clutch basket ( 21 ) rotatably with the first intermediate shaft ( 19 ) connected is. Power split transmission according to claim 2, characterized in that the first output clutch for forward drive (K _V1 ) and the output clutch for reverse drive (K _R ) coaxial with the output shaft ( 8th ) are arranged so that a driver element of the two output clutches (K _V1 , K _R ) each rotatably with a trained as a loose wheel output wheel ( 23 ' . 26 ' ) of the associated output stage (S _V1 , S _R ) is in communication, and that the common clutch basket ( 21 ' ) rotatably with the output shaft ( 8th ) connected is. Power split transmission according to one of claims 1 to 4, characterized in that the second output clutch for forward travel (K _V2 ) coaxially over the second intermediate shaft ( 20 ) is arranged such that a driver element of the second output coupling (K _V2 ) rotatably with an input gear designed as a loose wheel ( 27 ) of the second output stage (S _V2 ) is in communication, and that an associated clutch basket ( 29 ) rotatably with the second intermediate shaft ( 20 ) connected is. Power split transmission according to one of claims 1 to 4, characterized in that the second output clutch for forward travel (K _V2 ) coaxially over the output shaft ( 8th ) is arranged such that a driver element of the second output coupling (K _V2 ) rotatably with a formed as a loose wheel output wheel ( 28 ' ) of the second output stage (S _V2 ) is in communication, and that an associated clutch basket ( 29 ' ) rotatably with the output shaft ( 8th ) connected is. Power split transmission according to one of claims 1 to 6, characterized in that the turning output stage (S _R ) and the second output stage (S _V2 ) are arranged axially adjacent to each other, and that the second output clutch for forward drive (K _V2 *) together with another clutch (K _R *) of the turning output stage (S _R ) in a common switching package ( 30 ) is arranged with a sliding sleeve, by means of which the adjacent drive wheels ( 26 ' . 28 ' ) of the second output stage (S _V2 ) and the turning output stage (S _R ) alternately via the output clutch for reverse drive (K _R ) with the associated drive shaft ( 8th ) are connectable. Power split transmission according to claim 7, characterized in that the clutches (K _V2 *, K _R *) of the common switching package ( 30 ) are designed as unsynchronized jaw clutches. Power split transmission according to claim 7, characterized in that the clutches (K _V2 *, K _R *) of the common switching package ( 30 ) are designed as friction-synchronized jaw clutches. Power split transmission according to one of claims 1 to 9, characterized in that at the same size, via the two clutches (K1, K2) switchable speed ranges of the first and second coupling shaft ( 15 . 16 ) the ratio of the ratio of the first output stage (S _V1 ) to the ratio of the second output stage (S _V2 ) is four (i _V1 / i _V2 = 4). Power split transmission according to one of claims 1 to 4, characterized in that an additional countershaft ( 31 ) is provided, which via an associated Endabtriebsstufe (S _X ) with the output shaft ( 8th' ) is in driving connection, and at least on the second output stage (S _V2 ') and the associated second output clutch for forward drive (K _V2 , K _V2 ') with the second intermediate shaft ( 20 . 20 ' ) is connectable. Power split transmission according to claim 11, characterized in that the second output stage (S _V2 ') axially on the output side between the coupling gear ( 6 ) and the group of the first output stage (S _V1 ) and the turning output stage (S _R ') is arranged. Power split transmission according to claim 11, characterized in that the second output stage (S _V2 ') axially on the input side before the coupling gear ( 6 ) is arranged. Power split transmission according to one of claims 11 to 13, characterized in that the second output clutch for forward travel (K _V2 ) coaxially over the second intermediate shaft ( 20 ) is arranged such that a driver element of the second output coupling (K _V2 ) rotatably with an input gear designed as a loose wheel ( 34 ) of the second output stage (S _V2 ') is in communication, and that an associated clutch basket ( 29 ) rotatably with the second intermediate shaft ( 20 ) connected is. Power split transmission according to one of claims 11 to 13, characterized in that the second output clutch for forward travel (K _V2 ') coaxially over the countershaft ( 31 ' ) is arranged such that a driver element of the second output clutch (K _V2 ') rotatably with a formed as a loose wheel output wheel ( 36 ' ) of the second output stage (S _V2 ') is in communication, and that an associated clutch basket ( 29 '' ) rotatably with the countershaft ( 31 ' ) connected is. Power-split transmission according to one of claims 11 to 15, characterized in that with the same size, via the two clutches (K1, K2) switchable speed ranges of the first and second coupling shaft ( 15 . 16 ) the ratio of the ratio of the first output stage (S _V1 ) to the product of the ratios of the second output stage (S _V2 ') and the final output stage (S _X ) is four (i _v1 / (i _V2 ' * i _X ) = 4) ,