DE202017004555U1 - Power split transmission for a mobile work machine for simultaneous, regulated power output for driving the vehicle and the ancillaries - Google Patents

Abstract

Power split transmission 1 of a mobile machine with a traction drive motor and a vehicle transmission, comprising a planetary gear 10 with two axle shafts 3,6 and a gear 8 which is connected to an external toothing of a ring gear 4, and a gear 9, which is connected to an external toothing of a planet carrier 5 is, characterized in that an axle shaft 3 is connected to a sun gear 11 and ancillaries 20 of a work machine via a ring gear 4 and a gear 8 are driven, with a power supply to these ancillaries 20 by a control and regulating member 16, 23 is controllable, that the travel drive of this work machine via an axle 6, which is connected to a planet carrier 5, which in turn is connected via planetary gears 21 to an internal gear of a ring gear 4, takes place that a gear 9, a braking force or a driving force to a planet carrier 5 and an axle 6 for Driving speed control can be applied, that via a gear 9, a driving direction reversal is possible that via a vehicle transmission by adjusting the vehicle engine speed, the power supply by changing the speed and torque of the axle 3 to the planetary gear 10 is adjustable and that for applying a braking force to a gear 8 and / or a gear 9 at least one hydraulic brake wedge 23 in the transmission housing is arranged so that by a entrainment of hydraulic oil through the gears 8 and 4 and / or the gears 9 and 5 in a pressure increasing space 28 which is enclosed by the gears 8 and 4 and the brake wedge itself and / or the gears 9 and 5 and the brake wedge itself, comes to a pressure increase, which then leads to a braking force on the gear 8 and / or the gear 9

Description

The invention relates to a transmission for a work machine as it is known, for example. For the elimination of oil and other extreme pollution of traffic areas. Characteristic of such machines is that the actual cleaning device and the associated process engineering (ancillary equipment) are mounted on and / or on a carrier vehicle, which should quickly get to the place of use for reasons of cost (driving mode), eg DE 10 2010 027 314 , Therefore, these vehicles have a commercial engine as a drive unit, while the power is transmitted in a known manner via a clutch, a vehicle-mounted gearbox and a propeller shaft to the axles of the vehicle; This powertrain guarantees relatively high driving speeds. During the use of the cleaning machine, however, this drive train is not very suitable, since the cleaning device on the vehicle requires a very low and constant speed (working mode). Therefore, such vehicles have a so-called hydraulic hydrostatic drive as he, for example, from DE 3941024 is known.

Recent considerations aim to separate the propeller shaft into two drive subshafts, which are then connected via a power split transmission. In driving mode, these two drive part shafts are rigidly connected in the transmission and the ancillaries are not driven. In working mode, the two drive part shafts are separated and the entire engine power is used, for example, to drive a generator or a hydraulic pump via the first drive part shaft. By means of electric motors or hydraulic motors all auxiliary consumers of the vehicle and the second drive part shaft are then driven to the vehicle drive.

In DE 10 2014 001 020 such a drive train is described; Here, three clutches, eg. Electromagnetic clutches or pneumatically actuated clutches are installed in the drive train (propeller shaft) of a carrier vehicle with the built procedural components for the implementation of the work functions, while the output side after the vehicle transmission initially a driven clutch as a closing clutch, then a clutch and finally realized a drive clutch as a lock-up clutch. However, such an arrangement of the clutches can also be realized with a hydraulic system, wherein a hydraulic load can then be a power generator, which guarantees the electrical supply of the procedural components. The power flow thus takes place with the disconnect clutch (working mode) in the bypass of the first drive part shaft and the output coupling via the power take-off to the drive clutch and the second drive part shaft and to the drive of the ancillaries. When the disconnect clutch is closed (drive mode), the power flow takes place directly from the first drive part shaft to the second drive part shaft, so that virtually the complete propeller shaft train is restored.

Another embodiment of this technical solution is in EP 15700699.0 specified. Here, inter alia, it is proposed to transfer the power flow via the power take-off by means of a differential gear to the drive clutch, which can be acted upon by a friction element on the differential, which can be designed as a simple differential, that between the first axle and the second axle sets a different speed. This succeeds when the first axle of such a differential gear is driven by the output clutch and the power take-off and the second axle transmits its torque to the drive clutch. The friction force is adjustable. The higher it is, the lower the rotational speed of the second, connected to the drive shaft shaft of such a differential gear relative to the rotational speed of the first axle shaft. About the same power take-off, the other consumers of the working machine are supplied with drive power.

In DE 000002810086 is also a power split transmission with a planetary gear differential, which includes at least three gear members, such as sun gear, web and ring gear described, each with at least one of these gear members a transmission input shaft with another transmission output shaft and a third gear member for controlling the direction of rotation and speed of the same in both directions as a pump or motor operable displacement machine or operated in four-quadrant electric machine (= control engine) is coupled to a second operable as a pump or motor displacement machine or a second operable in four-quadrant electric machine, which is energetically coupled to the control engine.

In US 020110230296 a similar invention is disclosed as in DE 000002810086 , Here, a sun gear of a first planetary gear is connected to an input shaft. The planet carrier of the first planetary gear is connected to the sun gear of a second planetary gear and a first pump / motor. The ring gear of the first planetary gear is connected to a second pump / motor and the ring gear of the second planetary gear is connected to an output shaft. A first clutch of the transmission is for connecting and separating the planet carrier from the second planetary gear and the ring gear provided by the first planetary gear and a second clutch for connecting and disconnecting the planet carrier from the second planetary gear with a fixed point.

The technical solution according to EP 15700699.0 has the disadvantage that permanently energy is "destroyed" by the friction element, since it is constantly engaged, and it can lead to unacceptably high temperature developments. Further, in addition to the vehicle-side transmission and the power split transmission further transmission / clutches are required or it is, for example, complex hydraulic systems for alternative propulsion required. In the implementation of this solution, it therefore leads to an unnecessary weight and cost increase. In the EP 15700699.0 . DE 000002810086 and US 020110230296 In addition, inventions sketched have no evidence of how a force can be exerted on individual gears within the transmission. The imprint of a braking force within the transmission has the great advantage that the traction drive and the drive of the ancillaries can be realized without an external hydraulic system.

Therefore, this invention has for its object to overcome these disadvantages; This is achieved by all required to operate the machine drives over the vehicle transmission and another planetary gear can be realized, the "friction" mainly by the load of the ancillaries (= drive power demand of the ancillaries) and the structural installation of a component in the transmission itself, about that a braking force can be impressed on certain gears takes place. It should be noted that when driving slowly down the machine with constant driving speed braking energy is fed back and at slow driving up the machine at a constant driving speed additional drive power is needed. In both cases, the ancillaries (= Arbeitsverrichtungsaggregate) must be constantly supplied with a set drive power and the drive power for the travel drive and ancillaries can be independently adjustable. This is achieved on the one hand by a change in the speed of the vehicle engine (= change in the power output of the vehicle engine) and on the other hand in the at least one control and regulating component, for example. A proportional valve, proportionate hydraulic oil to the hydraulic motor for driving the ancillaries passes and the remaining hydraulic oil on the traction drive side is used for an auxiliary drive. The object is achieved by a device according to claim 1. Further developments of the device are the subject of the dependent claims.

The invention is described below with reference to an embodiment with reference to the accompanying figures. Show it:

1 : 3D illustration of the power split transmission

2 : Process flow diagram for simultaneous, regulated power output for driving the vehicle and the ancillaries

3 : Installation of a control and regulation component

4 : Control and regulation component

An otherwise not shown in detail mobile machine includes in the illustrated embodiment in 1 the power split transmission 1 , consisting of a planetary gear 10 with the externally toothed planet carrier 5 and the internally and externally toothed ring gear 4 with the sun gear, not shown 11 and planet wheels 21 to drive the work machine itself and ancillaries, which are arranged on the work machine as Arbeitsverrichtungsaggregate. A first drive part shaft, not shown, connected to the vehicle transmission, also not shown, to the drive flange 2 connected, stuck with the first axle shaft 3 connected is. On this axle shaft 3 is the rotatable externally toothed sun gear 11 stored, the rigid via a dog clutch with the axle shaft 3 can be connected, in which a first sliding sleeve with claws in the claws of the sun gear 11 can engage by means of axial displacement. The sun wheel 11 is about the planet wheels 21 firmly with the likewise externally toothed ring gear 4 connected. The planet carrier 5 is rotatable on a second axle shaft 6 stored, which via the output flange 7 is connected to the differential gear of the drive axle. The planet carrier 5 can be rigid with the axle shaft via a dog clutch 6 be connected, in which a second sliding sleeve with claws in the claws of the planet carrier 5 can engage by means of axial displacement. The planetary gear 10 includes a third clutch, which is the two axle shafts 3 and 6 rigidly connect, provided the planet carrier 5 not with the axle shaft 6 and the sun wheel 11 not with the axle shaft 3 connected is. An externally toothed gear 8th is constantly with the externally toothed ring gear 4 connected. Another gear 9 is constantly with the externally toothed planet carrier 5 connected.

In 2 is the process engineering implementation of the simultaneous power control for traction drive and ancillaries shown. The gear 8th drives a hydraulic oil pump 12 at; the hydraulic oil then passes through the control and Control component, executed, for example, as a proportional valve 16 , proportionally over the mixing valve 17 to a hydraulic oil engine 13 , in turn, the ancillaries 20 drives. From this hydraulic oil engine 13 the hydraulic oil passes through the three-way valve 18 either to the hydraulic oil tank 15 or to the hydraulic oil component 14 , which in turn is stuck with the gear 9 connected is. From the hydraulic oil component 14 , which acts as a pump, passes the hydraulic oil through the control valve 19 to the hydraulic oil tank 15 or to the mixing valve 17 in front of the hydraulic oil engine 13 , The rest, from the control and regulation component 16 Outflowing hydraulic oil passes through the three-way valve 29 to the hydraulic component 14 Now acting as a motor, the gear 9 alternatively on the traction drive side. From the hydraulic component 14 the hydraulic oil reaches the hydraulic oil tank 15 ,

• 1. Die eine Kupplung im Planetengetriebe 10 ist geschlossen, so dass die beiden Achswelle 3 und 6 starr miteinander verbunden sind. Die beiden anderen Kupplungen sind geöffnet, d. h. das Sonnenrad 11 ist nicht mit der Achswelle 2 verbunden und der Planetenträger 5 ist nicht mit der Achswelle 6 verbunden. In diesem Fall ist die mobile Arbeitsmaschine im reinen Fahrmodus, da durch die starre Verbindung der beiden Achswellen, die ihrerseits über die beiden Flansche 2 und 7 mit den beiden Antriebsteilwelle verbunden sind, die gesamte Motorleistung der Arbeitsmaschine zum Antrieb der Antriebsräder zur Verfügung steht. Die Nebenaggregate 20 werden nicht angetrieben.
• 2. Im Arbeitsmodus, d. h. konstante, langsame Arbeitsgeschwindigkeit der mobilen Arbeitsmaschine und Antrieb der Nebenaggregate 20 sind die beiden Achswellen 3 und 6 getrennt und das Sonnenrad 11 ist mit der Achswelle 3 und der Planetenträger 5 ist mit der Achswelle 6 verbunden, d. h. der Durchtrieb vom Fahrzeuggetriebe zu den Antriebsrädern ist unterbrochen; die jeweils anstehende Motorleistung wird an das Planetengetriebe 10 übertragen, d. h. über die Achswelle 3 wird bei einer bestimmten, vom Fahrzeuggetriebe abhängigen Drehzahl ein bestimmtes Drehmoment übertragen, so dass am Hohlrad 4 die gesamte Motorleistung zur Verfügung steht und damit jeweils rd. 50% dieser Leistung für den Fahrantrieb über den Planetenträger 5 und den Antrieb der Nebenaggregate über das Zahnrad 8 genutzt werden kann.
• a. Mobile Arbeitsmaschine fährt mit geringer Geschwindigkeit ohne Antrieb der Nebenaggregate: Das am Hohlrad 4 anstehende Drehmoment wird anteilig über das Zahnrad 8 zum Antrieb der Hydraulikölpumpe 12 verwendet und das Proportionalventil 16 ist geschlossen, so dass das ganze Hydrauliköl über das Drei-Wege-Ventil 29 zum Hydraulikbauteil 14 gelangt, das als Motor wirkend das Zahnrad 9 antreibt und so hilfsweise den Fahrantrieb ganz oder teilweise übernimmt. Das Hydrauliköl strömt danach zum Hydrauliköltank 15 zurück
• b. Mobile Arbeitsmaschine steht mittels Fuß- oder Feststellbremse des Fahrzeugs mit Antrieb der Nebenaggregate (Anfahren): Das am Hohlrad 4 anstehende Drehmoment wird über das Zahnrad 8 zum Antrieb der Hydraulikölpumpe 12 verwendet und das Proportionalventil 16 ist geschlossen, so dass das ganze Hydrauliköl über das Drei-Wege-Ventil 30 zum Hydrauliköltank 15 gelangt. Dann werden die Nebenaggregate eingeschaltet und ziehen volle Antriebsleistung. In dem Fall öffnet das Proportionalventil 16 und das Hydrauliköl gelangt über das Ventil 17 zum Hydraulikmotor 13, der die Nebenaggregate antreibt. Danach gelangt es über das Ventil 18 zurück zum Hydrauliköltank 15; das Fahrzeug steht noch. Werden nun die Fahrzeugbremsen gelöst, so halbiert sich die Leistung und steht jeweils am Hohlrad 4 und dem Planetenträger 5 zur Verfügung. Um die Nebenaggregate weiter mit der erforderlichen Antriebsleistung zu versorgen, wird die Motorleistungsabgabe über das Fahrzeuggetriebe gesteigert.
• c. Mobile Arbeitsmaschine fährt mit geringer Geschwindigkeit mit Antrieb der Nebenaggregate, wobei der Leistungsbedarf des Fahrantriebs geringer ist als der Leistungsbedarf der Nebenaggregate: Das am Hohlrad 4 anstehende Drehmoment wird anteilig über das Zahnrad 8 zum Antrieb der Hydraulikölpumpe 12 verwendet und das Proportionalventil 16 ist teilweise oder ganz je nach Leistungsbedarf der Nebenaggregate 20 geöffnet, so dass anteilig das Hydrauliköl über das Mischventil 17 zum Hydraulikölmotor 13 und von dort über das Drei-Wege-Ventil 18 zum Hydraulikölbehälter 15 gelangt. Das restliche Hydrauliköl gelangt vom Proportionalventil 16 über das Drei-Wege-Ventil 29 zum Hydraulikbauteil 14, das als Motor wirkend das Zahnrad 9 antreibt und so hilfsweise den Fahrantrieb ganz oder teilweise übernimmt. Das Hydrauliköl strömt danach über das Ventil 19 zum Hydrauliköltank 15 zurück.

The following operating modes of the working machine are possible:

• 1. The one clutch in the planetary gear 10 is closed, so that the two axle shaft 3 and 6 are rigidly connected. The other two clutches are open, ie the sun gear 11 is not with the axle shaft 2 connected and the planet carrier 5 is not with the axle shaft 6 connected. In this case, the mobile working machine is in the pure driving mode, due to the rigid connection of the two axle shafts, which in turn over the two flanges 2 and 7 are connected to the two drive part shaft, the entire engine power of the working machine for driving the drive wheels is available. The ancillaries 20 are not driven.
• 2. In working mode, ie constant, slow working speed of the mobile machine and drive the ancillaries 20 are the two axle shafts 3 and 6 separated and the sun wheel 11 is with the axle shaft 3 and the planet carrier 5 is with the axle shaft 6 connected, ie the drive from the vehicle transmission to the drive wheels is interrupted; the respective engine power is applied to the planetary gear 10 transmitted, ie via the axle shaft 3 is transmitted at a certain, dependent on the vehicle gear speed a certain torque, so that the ring gear 4 the entire engine power is available and thus approx. 50% of this power for the traction drive via the planet carrier 5 and the drive of the ancillaries via the gear 8th can be used.
• a. Mobile machine runs at low speed without driving the ancillaries: The ring gear 4 Pending torque is proportional to the gear 8th for driving the hydraulic oil pump 12 used and the proportional valve 16 is closed, allowing all the hydraulic oil through the three-way valve 29 to the hydraulic component 14 which acts as a motor, the gear 9 drives and thus alternatively takes over the travel drive in whole or in part. The hydraulic oil then flows to the hydraulic oil tank 15 back
• b. Mobile work machine stands by means of foot or parking brake of the vehicle with drive of the ancillaries (start): The on the ring gear 4 Pending torque is transmitted through the gear 8th for driving the hydraulic oil pump 12 used and the proportional valve 16 is closed, allowing all the hydraulic oil through the three-way valve 30 to the hydraulic oil tank 15 arrives. Then the ancillaries are switched on and draw full drive power. In that case, the proportional valve opens 16 and the hydraulic oil passes over the valve 17 to the hydraulic motor 13 driving the ancillaries. After that it passes through the valve 18 back to the hydraulic oil tank 15 ; the vehicle is still standing. If now the vehicle brakes are released, the power is halved and is in each case at the ring gear 4 and the planet carrier 5 to disposal. In order to continue to supply the ancillaries with the required drive power, the engine output is increased via the vehicle transmission.
• c. Mobile work machine drives at low speed with drive of the ancillaries, the power requirement of the drive is less than the power requirement of the ancillaries: The ring gear 4 Pending torque is proportional to the gear 8th for driving the hydraulic oil pump 12 used and the proportional valve 16 is partly or wholly depending on the power requirements of the ancillaries 20 open, so that proportionally the hydraulic oil through the mixing valve 17 to the hydraulic oil motor 13 and from there via the three-way valve 18 to the hydraulic oil tank 15 arrives. The remaining hydraulic oil comes from the proportional valve 16 via the three-way valve 29 to the hydraulic component 14 Acting as a motor the gear 9 drives and thus alternatively takes over the travel drive in whole or in part. The hydraulic oil then flows over the valve 19 to the hydraulic oil tank 15 back.

If the driving speed is increased, the rotational speed of the second drive part shaft and the associated axle shaft increases 6 and the planet carrier 5 , At the same time the speed of the ring gear decreases 4 Accordingly, so that to compensate for the speed of the first drive part shaft and thus the first axle 3 and the sun wheel 11 is increased accordingly by an increase in vehicle engine speed to the ancillaries 20 continue to supply the same drive power

Now, for example, by a steep uphill driving the machine a higher torque on the planet carrier 5 needed, so the vehicle engine speed is further increased. This would also be the power supply for the power take-off via the gear 8th increase. In this case, the proportional valve 16 closed so far that only so much hydraulic oil to the hydraulic oil motor 13 can get to the power supply to the ancillaries 20 to keep constant. The excess hydraulic oil is, as described above, back to the auxiliary drive via the hydraulic component 14 and the gear 9 used.

Now increases the driving speed through a downhill, so is the planetary carrier on the downgrade 5 via the second drive part shaft and the axle shaft 6 an external, additional torque impressed. In order to keep the driving speed constant, without actuating the vehicle brakes, the planet carrier becomes 5 through the gear 9 braked. This is done by that of the hydraulic oil motor 13 coming hydraulic oil is no longer to the hydraulic oil tank 15 but via the three-way valve 18 and a 4/2-way valve 22 to the hydraulic oil component 14 that with the gear 9 connected, passes. The hydraulic oil component 14 acting as a hydraulic oil pump builds against the control valve 19 a pressure, so that the hydraulic oil depends on the torque of the planet carrier to be braked 5 over the mixing valve 17 again in front of the hydraulic oil engine 13 can be returned. The braking energy of the planet carrier 5 can thus drive the ancillaries 20 be used.

A reversing direction of the mobile work machine can also relatively easily on the gear 9 take place, in which a flow reversal of the hydraulic oil takes place. In such a case, hydraulic oil is delivered via the mixing valve 17 and over the control valve 19 as well as the 4/2-way valve 22 the hydraulic oil component 14 fed, acting as a hydraulic oil motor and due to a change in direction, via the gear 9 the planet carrier 5 drives in the opposite direction. The hydraulic oil passes from the hydraulic oil component 14 over the valve 18 to the hydraulic oil tank 15 ,

It will be apparent to those skilled in the art that a mechanical or electrical design of the problem to be solved is possible according to the same process principle. In this context, another detail is relevant to the invention. For example, if a purely mechanical-acting, so hydraulic oil-free mobile work machine or a work machine with hydraulic oil-free drive are running, the control and regulation components should expediently within the entire transmission 1 be arranged.

In 3 is the installation of a corresponding control and regulation component and in 4 the control and regulation component itself shown. The control and regulation component is as a hydraulic brake wedge 23 designed and used within the transmission 1 firmly between, for example, the cooperating gears 4 and 8th and or 5 and 9 installed, while the front sides of the gears are within the brake wedge opposite the brake wedge sides 27 sealed. Upon entry of a gear, respectively, the transmission oil, which is also used as hydraulic oil, through the teeth or through the interdental space via the hydraulic oil inlet ramp 26 and pressure increase surface 25 transported along, while the pressure increasing surface may be fluidly designed so that in the direction of rotation of the gears results in a reduction of the free cross-section or strike the teeth directly close to the pressure increasing surface 25 , Since the lateral surfaces are sealed, it comes in the pressure-increasing space 28 , Which is included by the two gears and the brake wedge to an increase in pressure, which then leads to a braking force on the two gears, and thus to a reduction of the respective speeds. To the speeds over the height of the braking force or the pressure in the pressure-increasing space 28 To be able to regulate, is in a lateral surface of the brake wedge 23 an opening 24 in the pressure booster room 28 provided, via the transmission / hydraulic oil via a control valve, not shown here, from the pressure increase chamber 28 can escape, so that on the valve position of this control valve, the pressure in the pressure-increasing space 28 and thus the braking force is adjustable. This from the pressure booster room 28 Escaping hydraulic oil is returned via the mixing valve 17 in front of the hydraulic motor 13 recycled. Elsewhere, not shown here, is the transmission from the hydraulic oil tank 15 to compensate again supplied hydraulic oil.

Alternatively, on the opening 24 be waived. In such a case, the pressure adjustment takes place in the pressure-increasing space 28 by a shift of the respective brake wedge 23 to the two gears 5 and 9 or 4 and 8th or in the opposite direction. By such a radial displacement of the free flow cross section between the gears and the pressure increasing surface 25 changed so that adjustable here by the distance shift, the back-flowing hydraulic oil amount controls the pressure in the pressure-increasing space. In such a case, then, not shown here, the hydraulic oil is cooled by an external cooler. The person skilled in the art will appreciate that such a hydraulic brake wedge can also be arranged at a different location between other gearwheels of the transmission.

LIST OF REFERENCE NUMBERS

1

Power split transmission

2

Drive flange for connecting the first drive part shaft to the vehicle transmission

3

First axle shaft

4

Ring gear with internal and external teeth

5

Planet carrier with external toothing

6

Second axle shaft

7

Output flange for connecting the second drive part shaft to the traction drive

8th

Gear for driving the ancillaries

9

Gear for regulating the driving speed when driving downhill

10

planetary gear

11

sun

12

Hydraulic oil pump

13

Hydraulic oil Motor

14

Hydraulic oil component, acting as motor or pump

15

Hydraulic oil tank

16

Control and regulating component: Proportional valve

17

mixing valve

18

Three-way valve

19

control valve

20

ancillaries

21

planet

22

4/2-way valve

23

Control component: Hydraulic brake wedge

24

Hydraulic oil outlet to the control valve

25

Booster surface

26

Hydraulic oil inlet ramp

27

Lateral sealing surface to the gear

28

Pressurizing space

29

Three-way valve

30

Three-way valve

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

• DE 102010027314 [0001]
• DE 3941024 [0001]
• DE 102014001020 [0003]
• EP 15700699 [0004, 0007, 0007]
• DE 000002810086 [0005, 0006, 0007]
• US 020110230296 [0006, 0007]

Claims (7)

Power split transmission 1 a mobile work machine with a traction drive motor and a vehicle transmission, comprising a planetary gear 10 with two axle shafts 3 . 6 and a gear 8th connected to an outer toothing of a ring gear 4 connected, and a gear 9 connected to an outer toothing of a planet carrier 5 is connected, characterized in that an axle shaft 3 with a sun wheel 11 is connected and ancillaries 20 a working machine via a ring gear 4 and a gear 8th be driven, with a power supply to these ancillaries 20 by a control and regulation component 16 . 23 it is controllable that the drive of this work machine via an axle shaft 6 that with a planet carrier 5 , in turn, about planet gears 21 to an internal toothing of a ring gear 4 Connected, connected, that takes place via a gear 9 a braking force or a driving force on a planetary carrier 5 and an axle shaft 6 can be applied to the vehicle speed control that via a gear 9 a direction of travel reversal is made possible that via a vehicle transmission by adjusting the vehicle engine speed, the power supply by changing the speed and torque of the axle shaft 3 to the planetary gear 10 is controllable and that for applying a braking force to a gear 8th and / or a gear 9 at least one hydraulic brake wedge 23 in the transmission housing is arranged so that by a entrainment of hydraulic oil through the gears 8th and 4 and / or the gears 9 and 5 in a booster room 28 Being trapped by cogwheels 8th and 4 and the brake wedge itself and / or the gears 9 and 5 and the brake wedge itself, comes to an increase in pressure, which then leads to a braking force on the gear 8th and / or the gear 9 leads Power split transmission according to claim 1, characterized in that this braking force is adjustable thereby, in the via an opening 24 Hydraulic oil, connected to an external control valve, can controllably escape from the transmission and this hydraulic oil through the mixing valve 17 in front of the hydraulic motor 13 is returned. Power split transmission according to claim 1, characterized in that this braking force is adjustable thereby, in which the distance of the brake wedge from the gears 8th and 4 and / or from the gears 9 and 5 is changed accordingly, so that hydraulic oil regulated over the pressure increasing surface 25 can flow back into the gear housing. Power split transmission according to claims 1 to 3, wherein a gear 8th a hydraulic oil pump 12 drives, characterized in that a control and regulation component 16 , designed as a proportional valve, just just the amount of hydraulic oil to a hydraulic oil motor 13 lets through to the respective power requirement of ancillaries 20 covered to cover. Power split transmission according to claims 1 to 4, characterized in that the rest of the control and regulation component 16 outgoing hydraulic oil via a three-way valve 29 , a 4/2-way valve 22 and a hydraulic oil component acting as a motor 14 and a gear 9 auxiliary is used for the vehicle drive, with a 4/2-way valve by a change in direction of the gear 9 a direction of travel reversal is adjustable. Power split transmission according to claims 1 to 5 for braking energy recovery, wherein a gear 9 the acting as a pump hydraulic component 14 drives, characterized in that by a hydraulic oil motor 13 via a 4/2-way valve 22 flowing hydraulic oil undergoes an increase in pressure and a control valve 19 and a mixing valve 17 in front of a hydraulic oil engine 13 is returned. A power split transmission according to claims 1 and 6, wherein a hydraulic component acting as a motor 14 a gear 9 drives, characterized in that a via a mixing valve 17 , a control valve 19 and a 4/2-way valve 22 inflowing hydraulic oil in the hydraulic component 14 undergoes a pressure reduction and a mixing valve 18 to the hydraulic oil tank 15 is recycled, with a control and regulation component 16 a correspondingly higher amount of hydraulic oil to the mixing valve 17 and via a 4/2-way valve by a change in the direction of rotation of a gear 9 a direction of travel reversal is adjustable.

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