WO2011154533A1

WO2011154533A1 - Belt-type running gear and running gear axle having belt-type running gears

Info

Publication number: WO2011154533A1
Application number: PCT/EP2011/059718
Authority: WO
Inventors: Johann Rainer
Original assignee: Raipro Gmbh
Priority date: 2010-06-10
Filing date: 2011-06-10
Publication date: 2011-12-15

Abstract

The present invention relates to a belt-type running gear (100), in particular for a running gear axle (1) of a vehicle having two such belt-type running gears (100). The belt-type running gear (100) comprises at least one outer diverting roller (10, 16) and one drive roller (9) or two outer diverting rollers (10, 16) and one drive roller (9) arranged between these and above the diverting rollers (10, 16). An endless belt (5, 6, 31) runs over said rollers. Furthermore, at least one support roller (12) is provided which is situated below the drive roller (9), which is suspended in a movable and/or sprung and/or damped manner and which serves for supporting a ground-side belt portion between the two diverting rollers (10, 16) or between the outer diverting roller (10, 16) and the drive roller (9). At least the outer diverting rollers (10, 16) and the at least one support roller (12) are assigned to a carriage (3, 4) and/or supporting frame (24, 34) which is movable about a horizontal pivot axis (D) arranged perpendicular to the running direction (FR) of the belt-type running gear (100) or of the land vehicle. The suspension points of the at least one support roller (12) on the carriage (3, 4) and/or supporting frame (24, 34) of the belt-type running gear (100) or of each of the two belt-type running gears (100) and/or of the common swing frame (2) of the running gear axle are sprung and/or damped independently of one another. Furthermore, the supporting frame (24, 34) may be supported against a component, which is fixed with respect to the frame, of the vehicle via a torque support (40, 46).

Description

G U RT B A N D LA U FW E R K U N D LA U FW E R KS AC H S E M I T G U RT B A N D LA U FW E R K E N

The present invention relates to a belt drive, in particular for a drive axle of a vehicle with two such belt drives, with the features of independent claim 1.

Land vehicles used for the transport of goods and freight and / or in agriculture usually have pneumatic tires which interface with the ground. The tires must on the one hand the

Support vehicle weight and on the other hand provide the necessary traction. In very heavy vehicles, which are used in rough terrain and on poor, possibly unpaved roads and paths, arise even with a variety of wheels and / or with relatively large tires

Surface pressures below the tire contact surfaces, which can lead to sinking of the wheels and possibly even to de-stabilization or tilting of the entire vehicle especially in yielding soil conditions. Reduced internal tire pressure can only slightly change this problem, since the tire load is reduced at significantly reduced tire pressure, as is desirable for driving on soft or moist farmland, so that the weight of the vehicle can no longer be supported , This concerns in particular vehicles with high loads, as they can be used, for example, as a heavy transporter for logs or for special operations.

Chain or belt drives represent a possible alternative for

Radfahrwerke is because with such a drive, the effective footprint significantly increase and usually also an improved tensile force transmission on soft and moist soils can be realized. Vehicles are increasingly being used instead of propulsion and training wheels with pneumatic tires

Have Gurtbandlaufwerke, since this compared to the contact surfaces of

Rubber wheels provide a larger footprint and also promise improved traction on soft ground. In this case, exclusively drives are used in practice, in which either all supporting and deflection rollers rigidly on one Drive carriage are mounted or maximum individual small idlers are hinged spring. The reason for this is that the known belt web drives require very high pretensioning forces of the straps in order to be able to absorb sufficiently high loads between the carrying rollers. Therefore, the belt drives have so far mostly rigidly mounted pulleys.

These rigidly mounted pulleys have the typical disadvantage of a very limited driving and Abrollkomforts against a wheels suspension, especially when driving on the road. Another and more serious disadvantage of the known drives is that the uprising loads occurring can not be distributed evenly on all support and pulleys. Only in the ideal case, with absolutely flat soil conditions, a uniform load distribution is given. However, running a support roller on a bump, it is overloaded and relieved others, so in turn create high loads on the floors.

A chassis for agricultural machinery with elastic straps is known from US 54 09 075 A, in which the wheels supporting on the ground each have a pneumatic suspension. The pneumatic spring elements are coupled with each other on the pressure side, in order to maximize their value

uniform pressure distribution of the roller and tread contact surfaces with changing soil conditions and uneven floors to allow. Another landing gear for agricultural machinery with elastic

Webbings is evident from DE 196 20 759 A1. The wheels of the chassis are each suspended from swing arms, which are supported by hydraulic actuators on the frame. The hydraulic actuators are operatively coupled together to achieve a spring action and at

ensure different ground conditions and bumps consistent ground pressures of the rollers can.

Finally, DE 601 00 536 T2 describes a belt drive for an agricultural tractor, which is intended to make it possible to adapt to changing ground conditions as well as to uneven surfaces by means of a sprung suspension of the rollers and caster frames. The suspension includes several

Air suspension systems over which the front and rear crawler frames or the individual rollers are supported. Other webbing drives for land vehicles are, for example, from the WO

2006/018215 A1, from WO 93/19975 A, from DE 199 19 959 A1, from US 53 16 381 A, from US 59 97 109 A, from DE 44 15 689 A1 and from DE 200 00 737 A1 known. In addition, US 55 03 238 A discloses another

Belt drive for a land vehicle.

The well-known spring systems for webbing or track drives allow the elastically suspended rollers while an improved pressure distribution of the effective chassis contact surfaces between the outer pulleys on uneven ground, but do not allow uniform pressure distribution over the entire length of the drive, so that even in the known chassis partially very high pressure peaks are introduced into the soil. In addition, as a significant disadvantage of many known belt drives uneven

Load distribution on the footprint of the bottom webbing portion has been recognized, which is related to the fact that the vehicles tend to rise at high loads, with the front lifts and especially the rear portion of the webbing drive must transmit the tensile force. This creates higher

Surface pressures on the ground as partially desirable.

All known drives, which are articulated hinged about a support shaft, generate by the introduced driving forces torques about the support shaft. To support these torques about the support shaft arise on the rearmost arranged in the direction of travel pulley additional contact forces. Thus, the uniform load distribution over the entire contact length and surface is largely prevented. Under very unfavorable conditions, there is a risk that a drive will rotate about the axle, causing a large increase in the vehicle or even its rollover about the transverse axis.

Particularly in the case of belt drives with form-locking drives (so-called "positive drive"), there is the problem that a large support surface for the belt is desired on the drive wheels for supporting the belt tension forces, whereby at the same time, however, the proportion of power components transmitted via frictional effects becomes relatively high This can lead to increased mechanical stress on the belt and thus to increased wear of the belt and all bearings of the drive. A first object of the present invention is to obviate the aforementioned drawbacks and to provide a webbing drive which allows a more even floor loading and moreover for higher

Driving speeds on a solid surface is suitable, preferably with increased ride and ride comfort is to be offered.

To achieve this first object, the invention proposes a drive axle of a land vehicle with two belt drives, each having at least two outer pulleys and a arranged between these and above the pulleys drive roller on the circumference of an endless webbing rolls, and at least one located below the drive roller Having sprung and / or damped suspended support roller for supporting a bottom belt section between the two pulleys. In this case, the outer deflection rollers and the at least one support roller one to a horizontal and perpendicular to the

Moving direction of the land vehicle arranged pivot axis associated with moving carriage, which is arranged on a swing frame, which is resiliently and / or attenuated connected to a main frame of the land vehicle. It is further provided that the suspensions of at least one support roller on the carriage of each of the two belt drives and the common swing frame of the drive axle are sprung and / or damped independently. Furthermore, two or more support rollers of the same or different size can be provided for supporting the bottom belt section between the two deflection rollers per carriage. The support rollers can each be resiliently supported and / or damped and supported by a swingarm bearing on the carriage. The axes of rotation of the support rollers can advantageously be arranged to be pivotable within a plane perpendicular to the direction of travel of the land vehicle. Furthermore, it may be advantageous if the support rollers

are arranged adjustable in height and can be lowered for a road trip against the outer pulleys to reduce the effective support surface of the bottom belt webbing section. A further variant of the drive axle according to the invention provides that the drive rollers are rotatably mounted respectively in the swing frame, which is suspended and / or dampened suspended on the main frame of the land vehicle. The Drive rollers can optionally be connected in each case via a differential gear with a combustion or electric motor drive or with a Hydrostatantrieb. It is also possible that the drive rollers are each driven directly by hydrostatic travel drives or electric drives. The drive axle according to the invention may, for example, be part of a land vehicle with two, three or more axles with belt web drives arranged thereon and / or rubber-tyred wheels. In this context, it can be particularly advantageous if the axle is connected to the main frame of the land vehicle via a portal slewing ring, so that increased mobility and improved maneuverability of the vehicle is provided. Thus, an embodiment variant of such a land vehicle, for example, similar to a conventional tractor, having a steerable front axle with two conventional wheels and a main load bearing rear axle with a drive axle according to the invention with

Belt drive has. This can be steerable, for example, via a portal slewing ring independently of the front axle. A particularly high load carrying capacity is obtained when a semi-trailer for heavy loads or almost any applications for carrying particularly heavy, long or bulky loads is anchored pivotally on the drive axle.

It should be mentioned at this point in addition, that in the present context usually of an endless webbing is mentioned. Thus, for example, an elastic webbing of a suitable material - in particular a

Elastomer material with or without reinforcing fabric or wire inserts - meant. As a webbing in the context of the invention, however, is also a crawler o. The like. In question, which can be optionally provided with damping pads. Another object of the present invention is to provide the above-mentioned

Avoid disadvantages of trolleys and to provide a belt drive and / or a chassis axle with at least two such belt drives available that allow a more uniform ground load and also suitable for higher speeds on a solid ground, preferably an increased ride and ride comfort are offered should. An additional third important objective of the present invention is to ensure as uniform a surface pressure as possible on the ground, in particular during field travel in a relatively soft and / or moist subsoil. To achieve these other objects, the invention proposes a belt drive, in particular part of a drive axle of a

Land vehicle with two belt drives can be. The webbing drive has at least one outer deflection roller and one drive roller or two outer ones

Pulleys and arranged between them and above the pulleys drive roller on the circumference of an endless webbing unrolls. Furthermore, the drive comprises at least one located below the drive roller, movable and / or sprung and / or attenuated suspended support roller for supporting a bottom belt section between the two deflection rollers and the outer guide roller and the drive roller. The drive, deflection and support rollers are assigned to a horizontal and perpendicular to the direction of travel of the land vehicle pivot axis movable support frame, which is pivotally connected to a main frame of the land vehicle. According to the present invention, the support frame is supported via a torque support against a frame-fixed component of the vehicle. This torque support establishes a hinged connection between a frame portion of the support frame located near the drive roller and a support axis of the vehicle frame.

The belt drive according to the invention can in particular be a part of a land vehicle with two, three or more axles arranged thereon

Belt drives and / or rubber tires.

Such a drive or belt drive according to the invention comprises i.d.R. a flexible belt, which serves to transfer driving forces of the vehicle to the ground and to support the vehicle load. Optionally, the belt of a flexible material such as reinforced plastic or even

There are steel links, which are connected by means of rotating bolts.

The entire belt drive is suspended pendulously around a suspension axle. In addition to the basic elements required for the drive like a

Output gear, a drive wheel, a support frame, a front deflection axis and various support rollers, this drive is characterized in particular by an additional moment support, by means of which the drive is supported against the support shaft, whereby all effective torques due to the introduced drive powers can be largely supported. The effect of such Torque support can basically be transferred to all drives of similar construction with steel links or plastic chains or plastic belt straps or the like.

The support frame is preferably suspended on the support shaft about its axis of rotation oscillating. Since the output gear is freely rotatably mounted in the support frame, an additional support is required to support a torque generated by the transmission, which is here formed by the torque arm, which supports the drive gear against the support shaft against rotation. When designing the bearing areas of the supporting frame, the belt and axle loads as well as the occurring speeds must be taken into account. On the housing side, e.g. a

Slide bearing can be chosen because the housing is only in the range of

Pendulum range of the drive can move, for example. To twist angle of about +/- 10 °. On the output side, the output shaft also takes on the load-bearing

Axis function, is to choose a roller bearing for the connection, as here at

correspondingly higher speeds also relatively high speeds can occur.

The mode of action of the torque support is explained below in its basic features. A tensile force generated by the output gear, which supports the webbing on the ground, in turn causes a torque of the drive about the axis of rotation of the support shaft. Due to the structure of the tensile force arises at the same time on the housing of the output gear, the housing torque, which wants to put the transmission 3 in rotation. However, this is prevented by the moment support by this by the support of the resulting support force on the support shaft

Fixed output gear and simultaneously generates a supporting torque that counteracts the drive torque. The working line distances between the support lever on the support shaft and the support lever on the housing with the support frame and the moment support form a parallelogram, as well as the working line spacings of the lever drive and the radius drive wheel with the support frame and the distance support axle to drive wheel also a parallelogram, the two stand out Moments on each other. This means that a normally occurring

Support force goes to zero and the weight distribution is kept uniform on the uprising length.

If the drive wheel diameter or the lever of the drive is changed, can be adjusted by adjusting the support lever on the axle and on Support lever of the output gear again balancing the moments of the drive and the supporting moments are generated. Due to the design as a parallelogram or approximate parallelogram, the effect remains largely unaffected by the up and down the drive to the support shaft. Optionally, between the axle and the support frame a

Suspension swing be interposed to spring the drive as such. In order to avoid any effects due to the deflection on the support torque, the Stüzkraft is transmitted to the suspension axle parallel to the suspension arm via a reversing lever and a support shaft side torque arm. The

Output gear is supported by the torque arm on the lever.

An advantage of such a variant is that by the deflection without

Influencing the mode of action, the geometric design of the leverage is freely selectable. Is e.g. too little space above the axle, the torque arm can be moved downwards or vice versa. The drive can optionally also be designed as a triangular drive, in which the drive wheel is mounted on a spring-loaded drive rocker. An advantage of this design is that the undercarriage, which is articulated via the pendulum points to the drive rocker, barely changed the distance to the drive wheel at their deflection in the support frame. The belt circumference of the belt around the front and the rear deflection axis and the drive wheel thus remains almost constant and unaffected by the compression travel. The drive can be flanged to any axle. The disadvantage, however, would be that the suspension rocker is influenced by an applied tensile force, but this can also be compensated by a moment support. Such a drive variant is particularly suitable for heavy harvester such as combine harvester, in which a large installation space is available and / or a large ground clearance is desired, so that the upper drive wheel 4 can be accommodated easily. The output gear can have a lateral input. However, the output gear can also be almost any other type of drive, e.g. A transmission with a hydraulic motor o. The like .. It is only important that the drive unit is freely rotatably mounted and is held by a support.

The mode of operation of the torque support according to the invention is as follows. By the over the drive wheel in the belt introduced tensile force and the lever of the Belt distance is in the drive rocker a moment about the axis of the

Drive swing generated. In order to apply the tensile force, a corresponding moment also arises on the housing of the output gear, which in turn acts supported on the support frame via the torque support; this in turn results in a counter-moment in the drive rocker. If the lever lengths for the support levers on the support frame and the support levers on the housing output gear are matched according to the drive wheel diameter and the belt spacing, the deflection of the drive rocker is unaffected by a tensile force. For the handling of a vehicle, it is important that the tensile force does not affect the

Springing takes place. The advantage of this is a quiet ride, which is e.g. It is important for an accurate cutting system guide on combine harvesters.

A drive wheel can fulfill two separate basic functions. On the one hand, the drive wheel is used to drive any webbing via a drive wheel core, which is designed according to the drive lugs of the belt.

Furthermore, on both sides of the drive wheel core each run roller areas may be arranged which are freely rotatably mounted about the central axis. The particular advantage of this design is that with very flat drives the drive wheel must be arranged in place of a mostly rear drive roller and thus also supporting loads must be absorbed by the drive wheel. The diameter of the entire drive wheel is practically the same over the drive range and the Laufrollenbreich or adjusted if necessary according to the specifications of the belt manufacturer. The width of the areas also depends on the particular design of the belt. The wider a belt is, the more important it is that the caster area securely supports the belt against loaded loads. An advantage is also that, when the rear wheel is used as a pulley, a large wrap angle results and many drive lugs of a webbing are engaged, which in turn simplifies and improves the power transmission.

For the function is especially important that the roller areas can rotate against the drive wheel and thus takes place no frictional engagement between the belt and the drive, due to the thus caused increased

Belt wear is to be avoided. Since the relative movement between

Drive wheel and pulley areas for the execution of the function but is very low, can be used during storage on a simple plain bearing. In principle, for example, a kind of slewing ring as a storage unit be used. For example, the castor wheels may have a sliding area. Optimized coatings can then be applied to the roller wheels for the roller function. The sliding region can also be designed as a roller bearing or the like. Important is the safe and stable transmission of the load forces in the drive wheel core with a smooth rotatability to each other. It is also advantageous flat as possible storage, so that unnecessary space is wasted, which is urgently needed for example for drive gear.

The invention will be explained in more detail below with reference to preferred embodiments with reference to the accompanying drawings. The examples serve to illustrate the invention, but are in no way limiting. The same and equivalent parts are the same in the figures

Reference numbers designated; a multiple explanation is partly omitted.

Fig. 1 shows a schematic perspective view of the basic structure of the drive axle according to the invention. Fig. 2 shows a schematic representation of the drive axle of FIG. 1, which is connected to a main frame of a vehicle.

FIG. 3 shows a detailed view of the drive axle according to FIG. 2.

Fig. 4 shows in a side view of the drive axle, the principle of

Supporting force compensation. Fig. 5 shows a rear view of the drive axle.

Fig. 6 shows a plan view of the drive axle.

Fig. 7 shows a section along a drive side.

Fig. 8 shows a further section along a drive side.

9 shows a perspective detail view of the drive axle of FIG

Drive axle.

Fig. 10 shows a perspective view of a carriage as a unit with all its components. Fig. 1 1 shows a carriage as a unit without support and pulleys from diagonally below.

Fig. 12 shows the carriage of FIG. 1 1 from the side.

Fig. 13 shows the carriage of FIG. 1 1 from below. Fig. 14 shows a section through a carriage with active second

Suspension stage.

Fig. 15 shows a section through the carriage with deactivated second suspension stage.

Fig. 16 shows a section through the carriage at the height of a

Short-stroke cylinder.

FIG. 17 shows a further section through the carriage according to FIG. 16 at the level of a short-stroke cylinder.

Fig. 18 shows the drive unit attached to another main frame. 19 shows the drive unit on an intermediate frame with a turntable for

Use as steering axle.

Fig. 20 shows a further variant of a carriage in a side view.

FIG. 21 shows the variant of the carriage according to FIG. 20 from below.

Fig. 22 shows the basic structure of an embodiment of a

drive according to the invention in a schematic perspective view.

FIG. 23 shows a perspective view of the drive according to FIG. 22 without webbing. FIG.

Fig. 24 shows a schematic side view of the webbing drive according to

Fig. 22. Fig. 25 shows a sectional view of a drive wheel of the drive. Fig. 26 shows a further variant of the belt drive in a schematic perspective view.

Fig. 27 shows a perspective view of the drive according to Fig. 26 without webbing. Fig. 28 shows a schematic side view of the webbing drive according to

Fig. 26.

FIG. 29 shows a further schematic side view of the belt drive according to FIG. 26.

Fig. 30 shows a further variant of a belt drive in a schematic perspective view.

FIG. 31 shows an inside of the belt drive according to FIG. 30 in a perspective view. FIG.

FIG. 32 shows a further schematic perspective illustration of the drive according to FIG. 30 and FIG. 31, but without webbing. Fig. 33 shows a part of a support frame of the drive according to Fig. 30 in a schematic perspective view.

FIG. 34 shows a schematic side view of the drive according to FIG. 30.

Fig. 35 shows an embodiment of a drive wheel of a

drive according to the invention in a schematic perspective view. FIG. 36 shows two further views of the drive wheel according to FIG. 35.

FIG. 37 shows a sectional view of the drive wheel according to FIG. 35. FIG.

FIG. 38 shows a detail section of a region of the drive wheel according to FIG.

35th For identical or equivalent elements of the invention, identical reference numerals are used. Furthermore, for the sake of clarity, only reference symbols are shown in the individual figures, which are required for the description of the respective figure. The illustrated embodiments are merely examples of how the device or method of the invention may be configured and are not an exhaustive limitation.

Advantageous variants of a drive axle according to the invention are shown in the following explained Figures 1 to 38 in a schematic manner. 1 shows a schematic perspective view of the basic structure of the drive axle 1 according to the invention as a complete unit. The drive axle 1 comprises a swing frame with drive 2, which is suspended on a (not shown here) land vehicle, a left carriage 3, a right carriage 4, a left webbing 5, a right webbing 6 and two suspension cylinders 7 and 7 '. The drive axle 1 is formed according to the present invention as a double-springed and support force optimized drive axle 1 of any land vehicle.

The schematic representation of FIG. 2 shows the double-springed, support force-optimized drive axle 1 according to FIG. 1 as a complete unit, which is connected to a main frame 8 of any vehicle or land vehicle. The suspension cylinders 7 and 7 'are preferably articulated in the direction of travel FR to the rear, as this is a better vibration and suspension behavior of the

Swing frame 2 allows. It should be noted that the as

Suspension cylinder 7 and T designated suspension elements can optionally also have means for vibration damping. Equally possible, however, are arranged separately from the suspension cylinders 7 and T.

Damping elements.

The detailed view of FIG. 3 again shows the double-springed,

support force optimized drive axle 1 as a complete unit, integrated into a main frame 8 of any vehicle. To recognize here are the pivot points A and A 'of the swing frame 2 with drive to the main frame 8 and the

Suspension cylinder 7 and 7 ', the swing frame with drive 2 against the

Support main frame 8. By not shown straps and also not shown left drive wheel 9, this is easily recognizable. Also recognizable in Fig. 3, that the two carriages left 3 and right 4 about the axis of rotation D are hinged to the swing frame with drive 2 hinged.

The schematic representation of Fig. 4 shows in a side view of the drive axle 1, the principle of Stützkraftkompensation. The effective torque of a carriage (here 3) about the articulation point D is compensated and is equal to zero, when the angle α and the angle ß, which are formed between the line of action W passing through the deflection axis 10 and the pivot point D, are equal. The line of action W is defined by the effective directions of the driving force F _A and the resulting tensile force development F _z , as illustrated in FIG. 4. If there is no torque, the support and deflection rollers next to the support loads from the

Weight load does not support any further forces. The advantageous to be achieved by the invention support force compensation causes the belt drive is not caused by driving forces to rise, but at all times rests on the floor over the entire surface, whereby a very good support load distribution can be achieved. For moving heavy loads in problematic terrain and on unpaved roads

Because of this, this is particularly advantageous. At the same time, however, suspension is not dispensed with, so that the vehicle is also suitable for higher driving speeds, for example for transport journeys on a fixed ground. These

Driving speeds can be 50 km / h or more. The schematic representation of FIG. 5 shows a rear view of the

Drive axle 1, the rear of the main frame 8 by the suspension cylinder 7 and 7 'is supported. These two cylinders 7 and 7 'represent the first of the two

They decouple the drive as a whole from the main frame 8. It makes sense here hydropneumatic suspension systems are used to support the high forces. However, it is also possible air spring systems or mechanical springs of different design, possibly also in combination with air springs or hydropneumatic spring systems.

The representation of the drive axle 1 according to FIG. 6 shows a section through the drive axle 1 at the level of the rotation axis D. It can be seen here again the articulation of the swing frame 2 at the articulation points A and A 'on the main frame 8 of any vehicle. In the swing frame 2, an arbitrarily configurable drive mechanism can be integrated. Further recognizable are the carriage left 3 and right 4, the support rollers 12 and the two straps 5 and 6. The illustration of FIG. 6 illustrates in particular how the carriages 3 and 4 are articulated via two forks in the swing frame 2 on the axis of rotation D.

The illustration of Fig. 7 shows a section along a drive side with active second suspension stage. In this second suspension stage, the support rollers 12 are moved over the two Kurzhubzylinder 15 and 15 'and a mechanism described below relative to the guide rollers 16 to a Umlenkrollenabstand to the bottom of S and S' down. Furthermore, the two short-stroke cylinders 15 and 15 'are in turn connected to hydropneumatic suspension systems (not shown here). Due to the different position of the support rollers 12 and the

Deflection rollers 16 to the bottom, the very flat inlet and outlet angles δ and δ 'arise for the webbing 5, resulting in a shortened footprint of L1.

The state of the drive 1 shown in Fig. 7 is intended to be used primarily for fast road travel. Due to the separate second suspension stage, which decouples the support rollers 12 again separately to the rest of the drive, all small and short bumps of roads and paths are cushioned by the support rollers 12 in an effective manner. Of particular advantage is that the support rollers 12 have a very small unsprung mass compared to the heavy overall drive, whereby the suspension behavior is significantly improved. Furthermore, the flat inlet and outlet angles δ and δ 'of the webbing 5 to the ground have a very positive effect on the wear of the belt. A travel of about 3 to 4 cm in practice is completely sufficient for this stage.

Fig. 8 shows a further section along through a drive side with inactive second suspension stage. Here are the short-stroke cylinders 15 and 15 'retracted, whereby the support rollers 12 and the guide rollers 16 are each at the same distance from the ground, resulting in the maximum uprising length L2. This state of the drive should be used primarily for use in the field or on unpaved roads for the soil-conserving high loads or high tensile forces. It can be dispensed with the second suspension stage, since the entire vehicle is still sprung over the first stage and also the softer ground in contrast to the paved road has a dampening effect. The perspective detailed view of FIG. 9 shows a drive axle of the drive axle 1. Shown is the formation of the swing frame 2 with drive. The drive can basically be designed arbitrarily, for example. As indicated here with differential and side gears. Also conceivable, however, are final drives with mounted hydro or electric motors. The swing frame 2 is itself a rigid unit, whereby the left and the right drive carriage 3 and 4 are guided exactly to each other, which positively influences the belt run. Next so that the drive axle 1 record in a suspension concept all occurring forces.

Fig. 10 shows again a perspective view of the carriage 3 or 4 as a unit with all its components. The left and the right carriage 3 and 4 are basically the same structure.

The perspective view of Fig. 1 1 shows a carriage 3 and 4 as a unit without support and pulleys from obliquely below. The construction shown is only possible from a total of four support rollers 12, otherwise no stable support of the loads would be possible, especially in the raised road driving (see Fig. 7).

The schematic representation of Fig. 12 shows the carriage 3 and 4 of FIG. 1 1 as a unit without support and pulleys from the side. To recognize here are the rotation and bearing points B and B 'of the intermediate rockers 20 and 20' and the rotation and bearing points C and C of the axle rockers 19, where the

Pendulum axes 18 are arranged. The fact that two pendulum axles 18 are mounted on a transversely mounted to the direction of travel FR axle swing 19 and these in turn can oscillate longitudinally to the direction FR to the swingarm 19, the support load is always evenly distributed to all support rollers 12 within given limit stops. Next, this arrangement when driving on road a full-surface contact of the belt 5 or 6 to the road safely, which in turn has a very positive effect on the belt wear.

The illustration of Fig. 13 shows the carriage of FIG. 1 1 as a unit without support and pulleys from below. Recognizable here are the axes of rotation M and M 'of the pendulum axes 18th FIG. 14 shows a section through a carriage 3 or 4 with an active second suspension stage. Recognizable here are the extended Kurzhubzylinder 15 and 15 'with the cylinder stroke, which results from the sum of the installation length EB and the short stroke K. By the articulation of the short-stroke cylinders 15 and 15 'between the drive frame 17 and intermediate rockers 20 and 20', these are down to the rotation and bearings B and B 'twisted. As a result, the to the

Between swing 20 and 20 'hinged axle swing 19 with the

Swing axles 18 and the support rollers 12 offset by the distance S down.

Gurtlängenänderungen in the second suspension stage must by the

Belt tensioning cylinder 14 are compensated, but are generally very low due to the short distances and do not represent a problem in practice.

15 shows a section through the carriage 3 or 4 with deactivated second suspension stage, recognizable by the retracted short-stroke cylinders 15 and 15 'with the cylinder stroke, which corresponds to the installation length EB. FIG. 16 shows a section through the carriage 3 or 4 at the level of one

Short-stroke cylinder 15 or 15 '. Visible here is the intermediate rocker 20, which is mounted in the fork of the axle swing 19. Behind the pendulum axis follows 18. In the illustration shown, the distance to the short stroke K between the

Intermediate rocker 20 and the carriage frame 17 recognizable, i. the carriage 3 or 4 is active in the second suspension stage. If necessary, a lateral inclination can be blocked via the cylinder stroke.

FIG. 17 shows a further section through the carriage 3 or 4 according to FIG. 16 at the level of a short-stroke cylinder 15 or 15 '. Visible here is again the intermediate rocker 20, which is mounted in the fork of the axle rocker 19, after which the swing axle 18 follows. Here, however, the short-stroke cylinder 15 is retracted and the intermediate rocker 20 abuts on the drive frame 17, i. the second

Suspension level is inactive. In this state, when the intermediate rockers 20 abut the drive frame 17, it makes sense to perform the support positively (here light wedge shape) to support the intermediate rocker 20 at high loads, especially to intercept side forces.

FIG. 18 shows the drive unit 1 attached to another main frame 21. This over a turntable 22 with an intermediate frame 23rd connected. The drive unit 1 is drawn in an angled position to show that a stop is given by the swing frame 2 at the same time against too much commute. The special advantage is that the drive can not turn over. FIG. 19 shows the drive unit 1 on an intermediate frame 23

Turntable 22 for use as a steering axle. The steering can, for example, via cylinders or a drive in the turntable done.

FIG. 20 shows a further variant of a carriage 24 in one

Side view. This carriage 3 or 4 has individually hinged pendulum axles 18 on individual rockers 25, which are each mounted at a pivot point b and moved by a Kurzhubzylinder 26 for each rocker arm 25 or cushioned. With this principle, almost the same effect can be achieved as with the variant, which was previously explained. The advantage is that even with three or two

Swing axles the principle of double suspension is displayed. The schematic perspective view of FIG. 21 shows the variant of FIG

Carriage 24 as shown in FIG. 20 from below.

The schematic perspective view of Fig. 22 shows the basic structure of an embodiment of a drive according to the invention, here one

Gurtbandlaufwerkes 100, with a flexible belt 31, which serves to transfer driving forces of a vehicle (not shown) on the ground and for supporting the vehicle load. Alternatively, the strap 31 may be made of a flexible material such as reinforced plastic or steel members connected by rotatable bolts.

The entire webbing drive 100 is suspended pendulously about a support shaft 30. In addition to the fundamentally required elements for the drive 100 such as a driven gear 32, a drive wheel 33, a support frame 34, a front deflection axis 36 and various support rollers 37, this drive is characterized in particular by an additional moment support 35, by means of which the drive 100 against the Support shaft 30 is supported, whereby all effective torques due to the introduced drive power can be largely supported. The effect of the moment support 35 not only applies to such

Belt drive 100, but can be largely on all other drives similar structure with steel link chain o. The like. Transfer.

The schematic perspective view of Fig. 23 illustrates the mechanical structure and the operation of the torque support. Visible here is the support frame 34, which is suspended on the support shaft 30 about its axis of rotation A _T pendulum. It can also be seen that the output gear 32 with its central axis Aa, as it is freely rotatably connected via the bearing areas 5a and 5b of the support frame 34 in the support frame 34. Since the output gear 32 is freely rotatably mounted in the support frame 34, an additional support is required to support a torque generated by the transmission 3, here by the

Torque support 35 is formed, which supports the drive gear 3 against the support shaft 30 against rotation.

In the design of the bearing areas 5a and 5b of the support frame 34, the belt and axle loads and the speeds occurring must be considered. On the housing side, e.g. a sliding bearing can be selected, since the housing 3 can indeed move only in the range of the pendulum range of the drive 100, for example. Twist angle of about +/- 10 °. If the output shaft also takes over the load-bearing axle function on the output side, a roller bearing for the connection must be selected, since relatively high speeds can occur at correspondingly higher driving speeds.

The schematic side view of Fig. 24 is intended to illustrate the operation of the torque support. A generated by the output gear 32 tensile force F _z , which supports the webbing 31 on the ground, in turn causes a

Torque of the drive M _L about the axis of rotation of the axle A _T. Due to the structure of the tensile force F _z , the housing moment M _G is produced simultaneously on the housing of the output gear 32 and the gear 3 is set in rotation. However, this is prevented by the moment support 35 by this fixed by the support of the resulting support force F _M s on the support shaft 30, the output gear 32 and at the same time generates a support torque M _s , which counteracts the drive torque M _L. Form the effective line distances between the support lever on the support shaft L _M T and the support lever on the housing L _M A with the support frame 34 and the Momentum support 35 a parallelogram, and the effective line distances of the lever drive L _L and the radius drive wheel Ra with the support frame 34 and the distance support shaft to drive A _L ^* also a parallelogram, the two moments M _L and M _s cancel each other. This means that a normally occurring support force F _s goes to zero and the weight distribution on the

Riot length A _L is kept uniform.

If the drive wheel diameter or the lever of the drive L _{L is} changed, a compensation of the moments of the drive M _L and the support moments M _s can be generated by appropriate adjustment of the support lever on the support shaft L _MT and the support lever of the output gear L _M A. Due to the design as a parallelogram or approximate parallelogram remains through the up and

Pendulum of the drive 100 to the support shaft 30, the operation largely unaffected.

The schematic sectional view of Fig. 25 by the drive wheel 33 with output gear 32 also illustrates the belt 31, the bearing portions 34a and 34b of the support frame and the central axis of the drive Aa. Furthermore, a selected via this axis central input E _{z is} recognizable ..

In this example, the input E _{z is placed} centrally in the axis of the drive Aa. Thus, no lever length for a supporting force of a drive torque is given more, ie the drive torque M _L is not significantly affected and the transmission ratio of the output gear 32 is irrelevant to the function of the torque support.

The schematic perspective view of Fig. 26 shows another

Formation of a belt drive 100 with inventive

Torque support. In this variant, a suspension rocker 38 is interposed between the support shaft 30b and the support frame 34c to spring the drive 100 as such. In order to avoid any effects due to the deflection on the support torque, the Stüzkraft is transmitted parallel to the suspension arm 38 via the reversing lever 39 and the support shaft side torque arm 40 on the support shaft 30b. The output gear 32a (shown here with offset drive) is supported by the torque arm 35a on the lever 39. The advantage here is that the deflection without influencing the

Mode of action, the geometric design of the leverage is arbitrary. Is e.g. too little space over the axle, the torque arm 35 can be moved down or vice versa. The schematic perspective view of FIG. 27 shows that in FIG. 26

described drive 100 without belt 31 for clarity. It can be seen here in particular that the axis of the reversing lever 39 with the axis of the

Suspension rocker A _{s is} identical.

The side view of Fig. 28 shows the drive 100 described in Fig. 26 from the outside and illustrates the function of the suspension. Here, the suspension rocker 38 swings about the axis of the suspension arm A _s in the support frame 34 c and is simultaneously supported by the suspension cylinder 41 against the support frame 34 c. The axis of rotation A _T connected to the support shaft 30b is thus decoupled from the drive. With regard to this type of suspension, however, it should be mentioned that it is already known from the prior art.

The further schematic side view of FIG. 29 once again shows the drive 100 described in FIG. 26 and its mode of action. Here it can be seen that two parallelograms are formed here; on the one hand from the output gear 32a and the lever 39 with the moment support 35a and the support frame 34c, with the hinge points articulation point on the gear housing M _A , the upper pivot point of the Umlenkhebels Mu, the bearing of the transmission about the axis of the transmission Aa in the support frame 34c and the Axis of the suspension arm A _s . Furthermore, here is the parallelogram of the suspension arm 38 and the bearing axis side

Torque support 1 1 with the lever 39 and the support shaft 30b recognizable, with the hinge points of the axis of the suspension arm A _s , the lower pivot point of the Umlenkhebels Mu ^* , the axis of rotation of the support shaft A _T and the point of articulation of the torque arm on the support shaft M _T.

The design of the lever lengths is ultimately determined again by the design of the drive wheel diameter, the lever for the drive L _L and the position of the drive and the length corrections required thereby. The further schematic perspective view of Fig. 30 shows a further embodiment of a belt drive 100 with an inventive

Torque support. Shown here is a drive 100 in the form of a triangle, in which the drive wheel 33 is mounted on a spring-loaded drive rocker 45. An advantage of this design is that the undercarriage 43, which is articulated about the pendulum points P to the drive rocker 45, barely changed the distance to the drive wheel 33 when springing them in the support axle frame 44. The belt circumference of the belt 31 about the front deflection axis 36 and the rear

Deflection axis 36a and the drive wheel 33 thus remains almost constant and unaffected by the compression travel. In the illustration, the drive is flanged to any support shaft 42. The disadvantage, however, would be that the suspension rocker is influenced by an applied tensile force, but this can also be compensated by a moment support. Such a drive variant is particularly suitable for heavy harvester such as combine harvester, in which a large installation space is available and / or a large ground clearance is desired, so that the upper drive wheel 33 can be accommodated easily.

The perspective view of FIG. 31 shows the drive 100 described in FIG. 30 from the inside. Visible here is the Tragachsrahmen 44 with its flange on any support shaft, the belt 31, the deflection axes 36 and 36a with the support rollers 37. Furthermore, the drive wheel 33 can be seen on a driven gear 32b, which rotatably mounted in the drive rocker 45 and on the Torque support of the triangle drive 46 must be supported.

Here is an output gear with lateral input drive shown. The

However, the output gear may also be a virtually random drive designed otherwise, e.g. A transmission with a hydraulic motor o. The like .. It is only important that the drive unit is freely rotatably mounted and is held by a support.

The schematic perspective view of FIG. 32 shows the drive 100 described in FIG. 30 without belt for a better overview, so that here the axis of the drive rocker A _A s can be seen around the support axle frame 44. The illustration of FIG. 33 shows the drive 100 in FIG. 30 described in FIG

Range of the drive 3b and its arrangement. Visible here is the

Support shaft frame 44 and the drive rocker 45 about the axis of the Drive rocker A _A s in the support shaft frame 44 is rotatably mounted and

opposite to the suspension cylinders 41 again against the

Support shaft frame 44 is supported. Next you can see how that

Output gear 32b is rotatably mounted in the bearing areas of the drive rocker 45a and 45b. Against a rotation of the output gear 32 b is the

Torque support 46 via the point of articulation of the torque arm on the support frame M _T on the support shaft frame 44 and the point of articulation of the torque arm on

Output gear housing M _A hinged to the output gear 32b.

A particular advantage of this variant is that the drive and the suspension of a drive can be summarized compact.

The schematic side view of FIG. 34 shows the drive 100 described in FIG. 30 and again illustrates the mode of operation of the torque support according to the invention. By introduced via the drive wheel 33 in the belt 31 tensile force F _z and the lever of the belt gap L _G , a moment M _A s is generated in the drive rocker 45 about the axis of the drive rocker A _A s. In order to apply the tensile force F _z , also arises on the housing of the output gear 32 a

corresponding moment M _G , which in turn supported by the moment support 46 acts on the support shaft frame 44; this in turn results in a

Counter moment to M _AS in the drive rocker. If the lever lengths for the support levers on the support frame L _M T and support levers on the housing output gear L _MA are matched according to the drive wheel diameter Ra and the belt spacing L _G , the deflection of the drive rocker 45 is unaffected by a tensile force F _z .

For the driving behavior of a vehicle, it is important that the tensile force F _z does not influence the compression travel. The advantage of this is a quiet ride, which is important, for example, for an accurate cutterbar guidance in combine harvesters.

The schematic perspective view of Fig. 35 shows one possible

Variant of a drive wheel with two separate

Basic functions. On the one hand, the drive wheel is used to drive any webbing via a drive wheel core 50, which is designed according to the drive lugs of the belt. Furthermore, on both sides of the drive wheel core 50 respectively Caster areas 51 and 51 a arranged, which are freely rotatably mounted about the central axis M _A c.

The particular advantage of this design is that in very flat drives (see Figure 1), the drive wheel must be arranged in place of a mostly rear drive roller and thus also supporting loads must be absorbed by the drive wheel.

The two views of Fig. 36 show the drive wheel of Fig. 35 again in side view (right) and top view (left). The diameter D of the entire drive wheel is practically the same over the drive range B _A and the Laufrollenbreich B _L and B _L ^* or adjusted if necessary according to the specifications of the belt manufacturer. The width of the areas also depends on the respective

Execution of the belt. The wider a belt is, the more important it is that the caster area securely supports the belt against loaded loads. An advantage is also that, when the rear wheel is used as a pulley, a large wrap angle results and many drive lugs of a webbing are engaged, which in turn simplifies and improves the power transmission.

The sectional view of Fig. 37 shows the drive wheel of Fig. 35. The

Separation points T and T ^* show schematically the rotatable connections between the drive wheel core 50 and the roller areas 51 and 51 a.

For the function is especially important that the roller portions 51 and 51 a can rotate against the drive wheel and thus no frictional engagement between the belt and the drive takes place, which is to be avoided due to the resulting increased Gurtverschleißes. Since the relative movement between the drive wheel portion 20 and roller portions 51 and 51 a for the execution of the function but is very low, can be used in storage on a simple slide bearing. In principle, for example, a kind of turntable could be used as a storage unit.

The detail section of FIG. 38 schematically shows the region of a separation point. At the drive core 20, e.g. the roller wheels 52, which have a sliding region G, held by means of a mounting ring 54 mountable by means of screws S. On the pulley wheels 52 can then be optimal for the roller function

Coatings 53 are applied. The sliding area G can also be called Roller bearing or the like. Be performed. Important is the safe and stable transmission of the loading forces in the drive wheel core 50 with a smooth rotatability to each other.

It is also advantageous to have a design which is as flat as possible, so that space is not unnecessarily wasted, e.g. is urgently needed for drive gear.

The features of the invention disclosed in the foregoing description, the drawings and the claims can be used individually or in any combination for the realization of the invention in its various

Embodiments of importance. The invention is not limited to the above embodiments. Rather, a variety of variants and modifications are conceivable that make use of the inventive concept and therefore also fall within the scope.

LIST OF REFERENCE NUMBERS

1 drive axis as a complete unit

2 swing frame with drive

3 carriages left

4 carriages right

5 webbing left

6 webbing right

7, 7 'suspension cylinder

8 main frame of any vehicle

9 drive wheel, drive roller

10 deflection axis, deflection roller

1 1 Drive mechanics

12 carrying rollers, support rollers

13 clamping axis

14 clamping cylinders

15, 15 'short-stroke cylinder

16 pulleys

17 carriage frame 18 pendulum axles

19 axle swingarm

20, 20 'intermediate swing

21 other main frames of any vehicle

22 turntable

23 intermediate frame

24 carriage frame (single suspension)

25 single swingarm

26 short stroke cylinder (single rocker)

30 axle

30b axle, sprung version

31 webbing, belt

32 output gearbox

32a output gear with off-center drive

32b output gearbox for triangular drive

33 drive wheel

34 supporting frame

34a bearing point on the support frame

34b gearbox side bearing on the support frame

34c supporting frame, sprung variant

35 moment support

35a gear-side torque arm

36 front deflection axis

36a rear deflection axis

37 carrying rollers

38 suspension swingarm

39 lever

40 supporting axle-side torque arm

41 suspension cylinder

42 axle with manual transmission

43 Undercarriage

44 supporting axle frame

45 drive rocker

45a bearing point in the drive rocker

45b gearbox side bearing in the drive rocker 46 torque arm, triangular drive

50 drive wheel core

51 Caster area, outside

51 a Roller area, inside

52 caster rim

53 coating

54 retaining ring

100 Belt drive A, A 'Linkage points Swing frame on the main frame

A _a central axis drive

A _T axis of rotation of the axle

A _L uprising drive

A _L ^* Distance between axle and drive wheel

A _s suspension suspension swingarm

AAS axle drive swingarm

D pivot pendulum axle carriage

F _A driving force

F _z Traction-resultant traction

F _s supporting force

F _M s force moment support

FR direction of travel

α angle 1

ß angle 2

S, S 'pulley spacing to the ground

δ, δ 'entry and exit angles

L1 insurrection length short

L2 uprising maximum

L _MT Length of support lever on the axle

L _M A Length Support lever on the housing of the output gearbox

L _L lever drive

L _G lever belt distance

B, B 'pivot points intermediate arms

B _A wide drive range

B _L Wide roller area B _L ^* Wide roller area

C, C pivot points axle swing

D drive wheel diameter

G sliding area

M, M 'axis of rotation of the pendulum axes

M _A Coupling point Torque support on the output gearbox housing

M _T articulation point moment support on the axle

My articulation point lever at the top

Mu * Steering point lever at the bottom

M _L moment drive

M _G torque transmission housing

M _s supporting moment

M _A s Moment drive rocker

M _Ac central axis

EB installation length

E _z central drive

K short-stroke

P pendulum point

Ra radius drive wheel

S screw area

T separation point 1

T ^* separation point 2

X form fit

b pivot point single rocker

W action line

Claims

Belt drive (100), in particular for a drive axle (1) of a land vehicle with two belt drives (100), the at least one outer deflection roller (10, 16) and a drive roller (9) or two outer deflection rollers (10, 16) and one between them and above the

Deflection rollers (10, 16) arranged drive roller (9), over the circumference of which an endless webbing (5, 6, 31) rolls, and the at least one below the drive roller (9) located, movable and / or sprung and / or damped Suspended support roller (12) for supporting a bottom side Gurtbandabschnitts between the two guide rollers (10, 16) and the outer guide roller (10, 16) and the drive roller (9), wherein at least the outer guide rollers (10, 16) and the at least a

Support roller (12) one, about a horizontal and perpendicular to the running direction (FR) of the webbing drive (100) or the land vehicle arranged

Pivoting axis (D) are associated with movable carriages (3, 4) and / or supporting frames (24, 34) which articulates with a main frame (21) of the

Landfahrzeuges connected or on a swing frame (2) is arranged, which is resilient and / or damped with the main frame (21) of the

Landing vehicle is connected, and wherein the suspensions of the at least one support roller (12) on the carriage (3, 4) and / or support frame (24, 34) of the Gurtbandlaufwerks (100) or each of the two Gurtbandlaufwerke (100) and / or the common Oscillating frame (2) of the drive axle are independently sprung and / or damped and / or wherein the support frame (24, 34) via a torque support (40, 46) is supported against a frame-fixed component of the vehicle.

The webbing drive of claim 1, wherein the torque support (40, 46) provides a hinged connection between a frame portion of the support frame (24, 34) near the drive roller (9) and a support shaft of the vehicle frame (21).

Belt drive according to Claim 1, in which each carriage (3, 4) has two or more support rollers (12) of the same or different size for the support of the carriage bottom side webbing section between the two pulleys (10, 16) are provided.

4. Belt drive according to one of claims 1 to 3, wherein the support rollers (12) in each case via a pivot bearing (19) on the carriage (3, 4) are supported and supported resiliently and / or damped.

5. Belt drive according to one of claims 1 to 4, wherein the axes of rotation of the support rollers (12) are arranged pivotably within a plane perpendicular to the direction of travel (FR) of the land vehicle.

6. Belt drive according to one of claims 1 to 5, wherein the support rollers (12) are arranged vertically adjustable and for a road trip against the outer deflection rollers (10, 16) for reducing the effective support surface of the bottom belt portion are lowered.

7. Belt drive according to one of claims 1 to 6, wherein the drive rollers (9) are each rotatably mounted in the swing frame (17) which is suspended and / or attenuated suspended from the main frame (21) of the land vehicle.

8. Belt drive according to one of claims 1 to 7, wherein the drive rollers (9) each have a differential gear with a combustion or

Electric motor drive or are connected to a Hydrostatantrieb.

9. Belt drive according to one of claims 1 to 8, wherein the drive rollers (9) are each driven directly by hydrostatic travel drives or electric drives.

10. Belt drive according to one of claims 1 to 9, wherein the axis is connected via a portal turntable with the main frame of the land vehicle.

1 1. Belt drive according to one of claims 1 to 10, part of a

A land vehicle having two, three or more axles with webbing drives (100) and / or rubber tired wheels disposed thereon.