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US20080084111A1 - Traveling Mechanism for Agricultural Machines and Off-Road Vehicles Having an Endless Belt -Band Traveling Gear and a Corresponding Belt-Band Traveling Gear - Google Patents

Traveling Mechanism for Agricultural Machines and Off-Road Vehicles Having an Endless Belt -Band Traveling Gear and a Corresponding Belt-Band Traveling Gear Download PDF

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Publication number
US20080084111A1
US20080084111A1 US11/659,865 US65986505A US2008084111A1 US 20080084111 A1 US20080084111 A1 US 20080084111A1 US 65986505 A US65986505 A US 65986505A US 2008084111 A1 US2008084111 A1 US 2008084111A1
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United States
Prior art keywords
belt
traveling gear
band
bogie
band traveling
Prior art date
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Abandoned
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US11/659,865
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English (en)
Inventor
Johann Rainer
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Deere and Co
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Individual
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Priority claimed from DE202004020124U external-priority patent/DE202004020124U1/de
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Assigned to HARAIN VERWALTUNGSGESELLSCHAFT MBH & CO. KG reassignment HARAIN VERWALTUNGSGESELLSCHAFT MBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: RAINER, JOHANN
Publication of US20080084111A1 publication Critical patent/US20080084111A1/en
Assigned to DEERE & COMPANY reassignment DEERE & COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HARAIN VERWALTUNGSGESELLSCHAFT MBH & CO. KG
Abandoned legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D55/00—Endless track vehicles
    • B62D55/08—Endless track units; Parts thereof
    • B62D55/104—Suspension devices for wheels, rollers, bogies or frames
    • B62D55/112—Suspension devices for wheels, rollers, bogies or frames with fluid springs, e.g. hydraulic pneumatic
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D55/00—Endless track vehicles
    • B62D55/08—Endless track units; Parts thereof
    • B62D55/104—Suspension devices for wheels, rollers, bogies or frames
    • B62D55/112—Suspension devices for wheels, rollers, bogies or frames with fluid springs, e.g. hydraulic pneumatic
    • B62D55/1125—Hydro-pneumatic or pneumatic, e.g. air-cushioned
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D55/00—Endless track vehicles
    • B62D55/08—Endless track units; Parts thereof
    • B62D55/14—Arrangement, location, or adaptation of rollers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
    • B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
    • B60G2206/011—Modular constructions

Definitions

  • the present invention relates to a traveling mechanism for agricultural machines and off-road vehicles having an endless belt-band traveling gear.
  • the invention further relates to a belt-band traveling gear, particularly a spring-mounted, belt-band traveling gear with optimum bearing strength specifications, said belt-band traveling gear being suitable inter alia for self-propelled agricultural machines and other off-road vehicles.
  • the invention relates to a ground vehicle having a spring-mounted belt-band traveling gear with optimum bearing strength specifications.
  • Ground vehicles used in agriculture usually comprise pneumatic tires, which create the interface to the ground.
  • the tires have to support the weight of the vehicle on the one hand while providing the required traction on the other.
  • very heavy vehicles for example, in self-propelled harvesters, relatively high surface pressures result below the contact surfaces in spite of very broad tires with six or more individual wheels.
  • These high surface pressures can lead to an impermissibly high soil compaction especially in wet farmlands.
  • Even a reduced internal pressure of tires cannot change much about this problem since in the case of a clearly reduced tire pressure as would be desirable per se for traveling on soft or wet farmlands, the load on the tires is reduced as a result of which the weight of the vehicle can no longer be supported.
  • This relates particularly to vehicles having a greatly fluctuating weight such as e.g. root crop harvesters or the like.
  • Chain traveling gears or belt-band traveling gears represent a possible alternative for wheeled traveling mechanisms since the effective contact surface can be increased distinctly using a traveling gear of this type, thus enabling an improved transmission of the traction force on soft and wet farmlands to be realized in most cases.
  • those vehicles Due to the increasing requirement of protecting the ground and particularly the farmlands used for agriculture from excessively high weight loads resulting from machines and vehicles, those vehicles are being used increasingly which comprise suitable belt-band traveling gears instead of drive wheels and support wheels having pneumatic tires. This is because the former offer a larger contact surface as compared to the tread contacts of rubber wheels and additionally promise an improved traction force on the soft ground.
  • those traveling gears are used exclusively, in which either all the carrier rollers and deflection rollers are mounted rigidly on a bogie or at most individual small carrier rollers are linked using spring mounting.
  • the reason for this is that the belt-band traveling gears known from prior art require very high pretensioning forces of the belts in order to absorb sufficiently large loads between the carrier rollers. Therefore the hitherto known belt-band traveling gears comprise deflection rollers that are mostly rigidly mounted.
  • a traveling mechanism for agricultural machines having resilient belts is known from U.S. Pat. No. 5,409,075 A, in which the track rollers supported on the ground each have a pneumatic suspension system.
  • the pneumatic suspension elements are coupled to one another on the pressure side in order to enable the most uniform possible pressure distribution of the contact surface of the track rollers and the belt in the case of varying ground conditions and ground unevenness.
  • the track rollers of the traveling mechanism are each suspended on rocker arms, which are supported against the frame by means of hydraulic control elements.
  • the hydraulic control elements are coupled to one another in an action-oriented manner in order to achieve a spring effect and to be able to ensure constant ground pressures of the track rollers with varying ground factors and ground unevenness.
  • DE 601 00 536 T2 describes a belt-band traveling gear for an agricultural tractor, which belt-band traveling gear is supposed to enable an adjustment to varying ground conditions and ground unevenness by means of a spring suspension of the track rollers and the track roller frames.
  • the suspension system comprises several air spring systems by means of which each of the front and rear crawler frames or the individual track rollers are supported.
  • the known spring systems for belt-band traveling gears or chain traveling gears enable an improved pressure distribution of the effective traveling mechanism contact surfaces between the outer deflection rollers in the case of an uneven ground surface by means of the resiliently suspended track rollers.
  • they do not enable any uniform pressure distribution over the entire length of the traveling gear, as a result of which very high pressure peaks are transmitted partially in the farmlands even in the case of traveling mechanisms known from prior art.
  • a priority objective of the present invention is to avoid the aforementioned disadvantages and to provide a belt-band traveling gear, which enables a more uniform ground loading and additionally offers increased driving and rolling comfort.
  • a spring-mounted belt-band traveling gear with optimum bearing load specifications for ground vehicles said belt-band traveling gear having the characteristics of the independent clause 1 , comprises at least two outer deflection rollers, over whose periphery an endless belt rolls off and also at least one support wheel or a supporting roller for supporting the belt section which is in contact with the ground, between both the deflection rollers.
  • Both the deflection rollers are mounted in a bogie in a manner that enables them to rotate, which bogie is supported against a body frame of the vehicle by means of a first fluidic suspension and/or damping unit.
  • the at least one supporting roller is supported on the bogie by means of a second fluidic suspension unit and/or damping unit.
  • the belt-band traveling gear according to the present invention comprises a fluidic coupling of the first fluidic suspension and/or damping unit, by means of which the bogie is supported against the chassis frame, with the second suspension and/or damping unit, by means of which the at least one supporting roller is mounted on the bogie.
  • endless belt-band has been mostly used in the present invention to mean a belt-band, it can also be meant to connote e.g. a resilient belt of suitable material—especially an elastomer material with or without reinforcing fabric inserts or wire inserts.
  • a crawler or the like which can optionally be provided with damping supports can also be used as a belt within the scope of the present invention.
  • the fluidic suspension and/or damping units within the meaning of the present invention can be, e.g. lever units, which are supported by means of suitable fluid cylinders with a springy or damping effect.
  • a pure suspension system can be implemented e.g. by means of a gas filling as the circumflowing fluid.
  • additional damping units e.g. hydraulic dampers or mechanical (friction) dampers or the like could be provided, if necessary.
  • the fluidic suspension and/or damping units could also be a part of a hydropneumatic suspension and/or damping system, in which the relatively slow circumflow times of a hydraulic fluid are used for vibration damping and in which the rapid response behavior and the compressibility of a suitable pressure gas are used for implementing a desired springing effect.
  • the belt-band traveling gear according to the present invention having the characteristics of the independent claim comprises at least two carrier or deflection rollers of the traveling gear which are mounted by means of rockers or another suitable bearing on the bogie in a manner that enables them to rotate.
  • Naturally more than two deflection rollers can also be provided if this is expedient and if the corresponding installation space is available.
  • the corresponding portion of load is applied on the individual carrier rollers preferably by means of suitable supporting elements, e.g. the fluidic units mentioned above or suitable supporting cylinders.
  • the carrier and deflection rollers, over which the endless belt-band is tensioned are preferably connected rigidly to the bogie or have a belt tension device integrated therein.
  • the belt-band traveling gear can be e.g. a triangular traction unit comprising a central or laterally offset, overhead drive wheel.
  • a triangular traction unit is particularly suitable for being adapted to already existing wheel suspensions in order to make a partly or completely crawler-mounted vehicle from a wheeled vehicle.
  • the belt-band traveling gear comprises two or more supporting rollers of the same or varying size, which are each arranged between both the deflection rollers for supporting the belt section, which is in contact with the ground.
  • the belt-band traveling gear comprises two or more supporting rollers of the same or varying size, which are each arranged between both the deflection rollers for supporting the belt section, which is in contact with the ground.
  • almost any number of supporting rollers can be arranged between both the outer carrier or deflection rollers which are supported preferably individually or also in pairs or groups against the bogie by means of second fluid elements.
  • the supporting rollers are each suspended or mounted so as to enable a definite twist of the preferably resilient belt.
  • This can be possible by means of a suitable swivelability of the rotation axes of the supporting rollers about a real or virtual swivel axis oriented approximately parallel to the longitudinal direction of the vehicle.
  • a sufficiently resilient belt it is possible in this manner to prevent the belt from digging into the ground with only one load-bearing edge in the case of a greatly uneven ground.
  • the pivoting angle of the supporting rollers can be limited, if necessary, in order to reliably prevent the belt from wearing.
  • this swivelability of the individual supporting rollers by which an improved traction can be achieved in certain driving situations.
  • This cant of the belt can be supported firstly by the above-mentioned horizontal deviation of individual or all the carrier rollers, by their intensified pressurization (see explanation below) or also by a combination of both the control interventions.
  • the bogie or the two, three, four or more bogies themselves can also be gimbal-mounted or suspended in any another way in order to enable a slope compensation for the vehicle body.
  • This slope compensation can be effected optionally by means of inclination sensors and associated settling circuits or manually by the driver.
  • the vehicle axle load to be supported is initially transmitted in a suspension arranged on the bogie, e.g. a rocker connected to the bogie in a manner that enables said rocker to rotate.
  • This rocker is then in turn supported against the bogie by means of one supporting cylinder or an appropriately constructive design of several supporting cylinders to prevent said rocker from twisting.
  • a system pressure dependent thereon is built up in the supporting cylinder/s, which usually are hydraulic or pneumatic cylinders.
  • this system pressure is now used for being applied to the supporting cylinders of the carrier rollers and to apply the same portion of axle load to every carrier roller taking into consideration all the lever and cylinder surface area ratios.
  • the active surfaces of the supporting cylinders for the rocker for absorbing the axle load and the active surfaces of the three supporting cylinders for the rotatably mounted carrier rollers must then be adjusted to the rockers taking the lever ratios into account so as to be able to support 1 ⁇ 5 of the applied axle load on each carrier roller in the case of the same system pressure in all the cylinders.
  • the advantage of a uniform ground loading over the entire contact surface of a belt-band traveling gear is thus ensured.
  • an accumulator usually a hydropneumatic reservoir—can be connected to the mutually supporting cylinder system.
  • a springy effect is also achieved advantageously and a corresponding belt-band traveling gear is decoupled from the associated vehicle frame, so that the highest driving and rolling comfort is possible.
  • the rocker designed for absorbing and transmitting said forces in the bogie must have a defined width and lever lengths that are intended for taking up distances to be specified.
  • the rocker is then attached so as to be offset laterally by a required measure, preferably towards the center of the vehicle. The operating mode of the overall system is however not affected thereby.
  • Varying operating conditions can be realized for a belt-band traveling gear by means of another design form of the pressure system—usually a hydraulic system according to the present invention.
  • the traveling gear is preferably operated with a spring effect, in which an accumulator is connected.
  • the system pressure also increases or drops in the case of a varying axle load, it may be expedient, e.g. to detect the displacement of the rocker for absorbing the axle load and to accordingly track the fluid volume in the system by means of a corresponding pressure source and power source. This practically corresponds to a level control system as has been realized already many times and therefore need not be described further.
  • a variant according to the present invention can provide an amplitude-dependent variation of the spring rate.
  • two or more accumulators can be provided, which can be connected or disconnected depending on the load condition of the vehicle.
  • an amplitude or the traveling gear rocker can be detected.
  • the vibration amplitude normally increases in the case of a larger vehicle load and greater ground unevenness and higher travel speed. This can be counteracted by reinforcing the pressure fluid system particularly by decoupling one of several accumulators.
  • a finer adjustment can be carried out by variably disconnecting one, two, or more accumulators from the pressure fluid system so as to achieve a variable spring rate, which can be adapted to the varying driving and operating conditions.
  • the variations mentioned above can also be made during travel particularly by means of a suitable settling circuit.
  • Another advantage is achieved according to the present invention by decoupling the supporting cylinders and impinging the rotatably mounted carrier rollers by a pressure source deliberately so that these carrier rollers are loaded or relieved of load accordingly.
  • a pressure source deliberately so that these carrier rollers are loaded or relieved of load accordingly.
  • the belt-band traveling gear according to the present invention is particularly suitable for self-propelling agricultural work machines, for forest machines and construction machines and also for other commercial vehicles and transport vehicles, which can be used on soft, resilient and/or uneven grounds and also on impassable terrains.
  • the advantages of the vehicles having conventional wheeled traveling mechanisms namely their flexibility, their relatively good maneuverability and the relatively high travel speed are predominantly influential during on-road operation or when traveling on paved dry grounds.
  • wheeled traveling gears reach their limits in the case of very high vehicle weights.
  • the belt-band traveling gear according to the present invention enables a very easily realizable, automatically controllable or manually adjustable slope compensation since a certain inclination can be compensated during travel uphill or downhill by a corresponding pressurization of the traveling gear supporting cylinders.
  • a camber compensation of the vehicle body can be achieved in an additional gimbal-mounted suspension or any other suitable suspension of the bogie preferably on the left and right side each independent of the other. This firstly leads to an improved driving comfort and secondly an increased tilt resistance and improved traction.
  • the present invention relates to a traveling mechanism, which is equipped with at least two belt-band traveling gears according to one of the previously described embodiments.
  • a vehicle provided with such a traveling mechanism could optionally comprise two, three, four or more such belt-band traveling gears.
  • an arrangement with two rear belt-band traveling gears and one or two front, steerable, pneumatic wheels is possible.
  • special-purpose vehicles are also feasible which comprise only one rear preferably centrally arranged belt-band traveling gear according to one of the previously described embodiments and two front wheels.
  • Traveling mechanisms with four belt-band traveling gears, of which two or even all are steerable, are also possible. Numerous modifications and variations are possible depending on the desired application of the vehicle or the traveling mechanism.
  • FIG. 1 shows a schematic drawing of a basic structure of a variant of the belt-band traveling gear according to the present invention.
  • FIG. 2 shows a schematic drawing of a section of the basic structure of the belt-band traveling gear shown in FIG. 1 .
  • FIG. 3 shows a schematic sectional view of the belt-band traveling gear.
  • FIG. 4 shows a lateral view of another variant of the belt-band traveling gear.
  • FIG. 5 shows a possible structure of the piping for connecting the elements of the belt-band traveling gear based on a schematic block diagram.
  • FIG. 6 shows a schematic perspective view of a rigid vehicle axle equipped with two belt-band traveling gears according to the present invention.
  • FIG. 7 shows another variant of the embodiment of a belt-band traveling gear according to the present invention, which is equipped with a double rocker for the bearing of a symmetrically designed bogie.
  • FIG. 1 shows the schematic diagram of a first variant of a basic structure of the belt traveling gear 10 , said basic structure being selected in the form of an isosceles triangle here, since this is an advantageous form with regard to the installation space in an agricultural vehicle (not illustrated).
  • the figure shows the lateral view of the bogie 12 on which the rear carrier and deflection roller 14 and the front carrier and deflection roller 16 are fitted tightly and mounted in a manner that allows them to rotate.
  • the front carrier and deflection roller 16 is provided with a suitable clamping device—here a suitable clamping cylinder 18 .
  • a suitable clamping device here a suitable clamping cylinder 18 .
  • a drive wheel 20 on the bogie 12 which drive wheel is to be designed according to the driving type selected e.g. mechanical or even hydraulic, but is not illustrated in detail here.
  • the wrapping of the preferably resilient belt 22 around the drive wheel 20 , carrier and deflection roller at the front 16 and carrier and deflection roller at the back 14 results in the basic shape of the belt-band traveling gear 10 .
  • small supporting rollers or carrier rollers 24 are visible which are each mounted on associated rockers 26 in a manner that enables them to rotate about rotation axes 28 .
  • the carrier rollers 24 are each then supported against the bogie 12 by means of a supporting cylinder 30 assigned to each carrier roller and by means of the rockers 26 .
  • FIG. 1 a carrying axle 32 of any vehicle can be seen which transmits the axle load F A into the rocker 34 of the traveling gear by means of a rotary bearing 36 using which the traveling gear rocker 34 is supported against the traveling mechanism carrying axle 32 .
  • the bogie 12 of the belt-band traveling gear 10 is mounted on the rocker 34 of the traveling gear in a manner that enables said bogie to rotate about the rotation axis 38 .
  • the traveling gear rocker 34 is supported by means of the traveling gear supporting cylinder/s 40 on a supporting axle 42 , thus preventing said traveling gear rocker from twisting due to the transmitted axle load F A .
  • the rotation axis 38 of the traveling gear rocker and the supporting axle 42 are either a component of the bogie 12 or fixedly connected thereto.
  • the transmitted axle load F A can be transmitted in the bogie 12 by the supporting force F ST applied by the traveling gear supporting cylinder 40 and the connection of the traveling gear rocker 34 .
  • a system pressure is built up in the traveling gear supporting cylinder 40 for achieving the supporting force F ST on the traveling gear, which system pressure then in turn for impinging the supporting cylinders 30 for the carrier rollers 24 by means of a piping and hose line system (not illustrated in detail here) as is shown schematically in FIG. 5 by way of example.
  • the transmitted axle load F A is distributed uniformly on all the carrier rollers 24 and also the front carrier and deflection roller 16 and the rear carrier and deflection roller 14 from which there results a uniform contact load F R of the carrier and deflection rollers 14 , 16 and 24 .
  • FIG. 2 schematically shows a section of the basic structure of a belt-band traveling gear 10 shown in FIG. 1 .
  • the axle load F A is transmitted in the traveling gear rocker 34 according to the invention by means of the rotary bearing 36 of the carrying axle.
  • the rotation axis 38 of the traveling gear rocker 34 is mounted rotatably on the bogie 12 .
  • the supporting cylinder 30 connected to the traveling gear rocker 34 is supported against the supporting axle 42 of the bogie 12 and thus prevents the traveling gear rocker 34 from twisting.
  • a supporting force F ST is generated on the traveling gear, which supporting force is dependent on the lever length (axle load) L A and the lever length (support load) L S and also the axle load F A transmitted by means of the traveling mechanism carrying axle 32 .
  • the system pressure required for the supporting force F ST on the traveling gear results on the basis of the selected cylinder diameter for the traveling gear supporting cylinder/s 40 and the active surface resulting therefrom.
  • FIG. 3 shows a sectional view of the belt-band traveling gear 10 in a plan view so that it is apparent that, e.g. in the exemplary embodiment shown in FIG. 1 , the traveling gear rocker 34 has a broad rocker B S for absorbing all the acting forces. Due to the arrangement of the drive wheel 20 , it is necessary in this case to offset the traveling gear rocker 34 then by a distance A S between the rocker and the center of the traveling gear. It makes sense to offset said traveling gear rocker 34 towards the center of the vehicle.
  • the connection to the bogie 12 is effected by the appropriately designed rotation axis 38 of the traveling gear rocker and the supporting axle 42 of the bogie 12 . Due to the broad rocker B S it is also possible to attach several traveling gear supporting cylinders 40 according to FIG. 3 , two supporting cylinders being attached in the exemplary embodiment illustrated.
  • FIG. 4 further shows a lateral view of the spring-mounted belt-band traveling gear 10 with optimum bearing load specifications in an alternative embodiment, namely in a so-called V-formation.
  • the figure shows that by means of a front carrier and deflection roller 17 of smaller diameter and a larger rear carrier and deflection roller 15 which can also simultaneously serve e.g. as a drive roller, a belt-band run can be drawn which permits the installation of the traveling gear rocker 34 centrally above the bogie 13 in the case of a bogie 13 that is likewise adapted to the requirements, so that there is no distance A S between the rocker and the center of the traveling gear (c.f. FIG. 3 ) or that this distance is equal to zero.
  • FIG. 5 shows the basic structure of a possible piping for connecting all the fluidic or hydraulic elements and thus the possible operating conditions of the belt-band traveling gear according to the present invention. It is apparent how the traveling gear supporting cylinder/s 40 , the carrier roller supporting cylinders 30 , an accumulator 48 and a pressure source P are initially interconnected according to the present invention by means of a piping and hose line system 50 .
  • the valves 52 , 54 , 56 and 58 are integrated in the piping and hose line system 50 , as is shown here schematically.
  • this system can advantageously be a hydraulic system.
  • the pressure system can comprise a gas or air as a pressure medium.
  • the following operating conditions of the belt-band traveling gear 10 are possible according to an exemplary embodiment of the present invention. If at first only the supporting cylinders 30 and 40 and also the accumulator 48 are interconnected, i.e. valves 52 and 56 are open, valves 54 and 58 are closed, then an axle load is distributed uniformly on the carrier rollers and an active suspension of the overall system is achieved simultaneously with the help of a hydropneumatically designed accumulator 48 . In the case of a constant axle load, the pressure source P need not be necessarily connected since there exists an approximately constant system pressure in the closed system.
  • the active suspension can be disconnected by disconnecting the accumulator 48 (valve 52 closed). Then only one fluid volume is exchanged between the supporting cylinders 40 and 30 according to the carrier roller movement, in the case of a system pressure determined by the axle load. The uniform distribution of the axle load is thus unaffected thereby.
  • the central carrier rollers 24 can be loaded or relieved of load, then this can take place by separating the traveling gear supporting cylinder 40 from the carrier roller supporting cylinders 30 .
  • the valves 56 and 54 are closed in doing so and valve 58 opens.
  • the loading of the carrier rollers 24 can be controlled by means of the pressure source P.
  • an increased loading of the carrier rollers located down-slope can take place so that the contact surface of the traveling gear is shortened, which can be advantageous to prevent lateral slippage or drifting.
  • the accumulator 48 can be connected to or disconnected from the traveling gear supporting cylinder 40 by opening or closing the valve 52 , which in turn corresponds to an operating condition with or without active suspension.
  • FIG. 6 illustrates a rigid vehicle axle 32 , which is equipped with two belt-band traveling gears 10 according to the invention corresponding to the variant of the embodiment shown in FIGS. 1 to 3 . It is apparent that instead of conventional wheels with pneumatic tires, the drive wheels 20 of the respective left and right belt-band traveling gears 10 are now connected to the hubs of the rigid carrying axle 32 of the vehicle.
  • the belt-band traveling gears 10 according to the present invention are thus basically suitable for the universal backfitting of existing wheeled traveling mechanisms.
  • FIG. 7 shows another variant of the embodiment of a belt-band traveling gear 10 according to the present invention, which belt-band traveling gear is equipped with a double rocker for mounting a symmetrically designed bogie 12 .
  • Both the similarly designed and largely symmetrically arranged traveling gear rockers 34 are coupled by means of the common bolt of the rotation axis 38 .
  • both the rockers 34 enclose a hydrostatic wheel hub motor 60 , which is coupled to a hydrostatic drive system of the vehicle (not illustrated) by means of a connection 62 .
  • the drive can also be configured by means of e.g. a switchable planetary gear or any other conventional mechanical method if necessary.
  • the carrier and deflection rollers 14 and 16 and also the carrier rollers 24 are each divided centrally and mounted on the centrally arranged, relatively narrowly designed bogie 12 .
  • the exemplary embodiment shows a spring-mounted, belt-band traveling gear 10 with optimum bearing load specifications, particularly for self-propelling agricultural machines and other off-road vehicles, in which belt-band traveling gear all the small carrier rollers 24 are connected to the bogie 12 by means of a rocker 26 in a manner that enables said carrier rollers to rotate about the carrier roller rocker rotation axes 28 .
  • Another characteristic is that every carrier roller rocker 26 and thus the small carrier rollers 24 are supported by means of a carrier roller supporting cylinder 30 on each carrier roller rocker 26 towards the bogie 12 .
  • the carrier roller supporting cylinders 30 are each mounted on the side of the bogie in the rotation axes 44 of the carrier roller supporting cylinder 30 on the bogie and in the carrier roller rockers 26 in the rotation axis 46 .
  • Another characteristic is that the first front deflection and carrier roller 16 and the last rear deflection and carrier roller 14 are each connected to the bogie 12 fixedly or by means of a clamping device with clamping cylinder 18 .
  • traveling gear 10 Another characteristic of the traveling gear 10 is that an axle load F A is transmitted initially in the traveling gear rocker 34 by the traveling mechanism carrying axle 32 via the rotary bearing 15 [sic: 36 ] of the traveling mechanism carrying axle, said rotary bearing being necessary for ground balance.
  • the traveling gear rocker 34 is in turn mounted rotatably on the rotation axis 38 of the traveling gear rocker and is supported on the opposing side by means of one or more traveling gear supporting cylinders 40 against the traveling gear supporting cylinder supporting axle 42 .
  • the axle load F A transmitted into the traveling gear rocker 34 is transferred to the bogie 12 .
  • the characterizing part is that corresponding to the lever ratios of the lever length axle load (L A ) to the lever length supporting load (L ST ), the traveling gear support cylinder/s 40 builds up a supporting force F ST on the traveling gear depending on the axle load F A .
  • F ST F A ⁇ L A /L ST holds true.
  • Another characteristic is that for achieving an equalization of the contact force F R of the carrier and deflection rollers, the traveling gear supporting cylinder/s 40 are then interconnected with all the carrier roller supporting cylinders 30 by means of a piping and hose line system 50 .
  • Another characteristic is that due to the involvement of the preferably hydropneumatic accumulator 48 , a spring effect of the overall system of the belt-band traveling gear is achieved in that the traveling gear rocker 34 and the traveling gear supporting cylinder/s 40 absorb corresponding vibrations.
  • An additional part of the exemplary embodiment is a spring-mounted, belt-band traveling gear with optimum bearing load specifications which belt-band traveling gear is designed as a triangular traction unit with a, centrally, overhead drive wheel 20 , wherein the traveling gear rocker 34 having a rocker width B S is mounted for installation reasons, i.e. lack of space such that it is offset by a center distance A S of the rocker from the center of the belt 22 . Though the traveling gear rocker 34 then absorbs the corresponding torsion, the interaction of the above-mentioned components is not affected thereby.
  • the center distance A S to the rocker is expediently selected to be smaller, if necessary even equal to zero.
  • Another part of the exemplary embodiment is a spring-loaded, belt-band traveling gear with optimum bearing load specifications in which belt-band traveling gear, the carrier roller supporting cylinders 30 , the traveling gear supporting cylinder/s 40 and the accumulator 48 are interconnected by means of the piping and hose line system 50 and the valves 52 , 54 , 56 and 58 in a manner so as to enable the following operating conditions.
  • a characteristic of an operating condition with active suspension is that all the elements, i.e. the carrier roller supporting cylinders 30 , the traveling gear supporting cylinders 40 and the accumulator 48 are connected to one another; the system pressure P is then adjusted accordingly depending on the axle load F A in the case of a filled system.
  • a position detection system is expediently integrated in the traveling gear supporting cylinder 40 or assigned thereto so that the system pressure P and thus the stroke can be tracked accordingly. Since these systems are already known from the prior art, these will not be explained in detail.
  • a characteristic of an operating condition with deactivated suspension is that only the traveling gear supporting cylinder/s 40 are connected to the carrier roller supporting cylinders 30 wherein the valves 52 , 54 and 58 are closed.
  • a system pressure P is built up depending on the axle load F A .
  • the carrier roller supporting cylinders 30 alone are connected to the pressure source and the system pressure P.
  • the accumulator 48 can be connected by means of the valve 52 to the traveling gear supporting cylinder 40 or it can be separated from the latter so that it is possible to drive selectively with or without the suspension.
  • control systems can also be developed, in which the previously mentioned different operating conditions (switch states of the valves etc.) for every individual traveling gear 10 or for every individual cylinder can be controlled individually.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
US11/659,865 2004-08-11 2005-08-11 Traveling Mechanism for Agricultural Machines and Off-Road Vehicles Having an Endless Belt -Band Traveling Gear and a Corresponding Belt-Band Traveling Gear Abandoned US20080084111A1 (en)

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DE202004012552.8 2004-08-11
DE202004012552 2004-08-11
DE202004020124U DE202004020124U1 (de) 2004-08-11 2004-12-28 Gefedertes, auflagekraftoptimiertes Gurtbandlaufwerk
DE202004020124.0 2004-12-28
DE102005035507.2 2005-07-26
DE102005035507 2005-07-26
PCT/EP2005/008716 WO2006018215A1 (fr) 2004-08-11 2005-08-11 Mecanisme de deplacement pour machines agricoles et vehicules tout-terrains a mecanisme de roulement a courroie continue, et mecanisme de roulement a courroie continue correspondant

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US20080084111A1 true US20080084111A1 (en) 2008-04-10

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US11/659,865 Abandoned US20080084111A1 (en) 2004-08-11 2005-08-11 Traveling Mechanism for Agricultural Machines and Off-Road Vehicles Having an Endless Belt -Band Traveling Gear and a Corresponding Belt-Band Traveling Gear
US12/574,267 Active 2027-10-13 US8147007B2 (en) 2004-08-11 2009-10-06 Traveling mechanism for agricultural machines and off-road vehicles having an endless belt-band traveling gear and a corresponding belt-band traveling gear

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US (2) US20080084111A1 (fr)
EP (1) EP1776268B1 (fr)
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US20120023881A1 (en) * 2010-07-30 2012-02-02 Dirk Speckamp Self-propelled harvesting machine
US20140138169A1 (en) * 2011-04-13 2014-05-22 Ryan James Fairhead Suspension assembly for personal tracked vehicle
US20140265198A1 (en) * 2013-03-15 2014-09-18 Kuhn North America, Inc. Bogie axle for a machine
US20150097361A1 (en) * 2012-06-27 2015-04-09 Louis-Philippe Rivard Mobile stabilisation device
US9033431B1 (en) 2010-06-30 2015-05-19 Camoplast Solideal Inc Track assembly for an off-road vehicle
US9505454B1 (en) 2011-06-13 2016-11-29 Camso Inc. Track assembly for traction of an off-road vehicle
US20170036714A1 (en) * 2015-08-04 2017-02-09 Camso Inc. Track system for traction of an agricultural vehicle travelling on fields and roads
US10246148B2 (en) 2014-04-25 2019-04-02 Ponsse Oyj Crawler-track unit, forest machine and forest machine assembly
US20190127104A1 (en) * 2017-11-02 2019-05-02 Krones Ag Glue supply for labeling unit with glue printer
EP3483048A1 (fr) * 2017-11-08 2019-05-15 CLAAS Industrietechnik GmbH Mécanisme de déplacement sur chenille pour un engin agricole
US10783723B2 (en) 2015-06-29 2020-09-22 Camso Inc. Systems and methods for monitoring a track system for traction of a vehicle
US10933877B2 (en) 2010-12-14 2021-03-02 Camso Inc. Track drive mode management system and methods
US11046377B2 (en) 2015-03-04 2021-06-29 Camso Inc. Track system for traction of a vehicle
US11077897B2 (en) 2015-10-23 2021-08-03 Camso Manufacturing Italy S.R.L. Track system for traction of a vehicle
US20210269106A1 (en) * 2020-02-27 2021-09-02 Claas Industrietechnik Gmbh Track drive of an agricultural production machine
US11225118B2 (en) 2018-04-19 2022-01-18 Naf Neunkirchener Achsenfabrik Ag Bogie for a forestry vehicle and vehicle with at least one bogie axle
US11835955B2 (en) 2017-12-08 2023-12-05 Camso Inc. Systems and methods for monitoring off-road vehicles
US12090795B2 (en) 2018-08-30 2024-09-17 Camso Inc. Systems and methods for monitoring vehicles with tires
USD1054458S1 (en) * 2022-01-13 2024-12-17 Soucy International Inc. Track assembly
US12254616B2 (en) 2018-08-30 2025-03-18 Camso Inc. Systems and methods for monitoring tracked vehicles

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WO2011154533A1 (fr) 2010-06-10 2011-12-15 Raipro Gmbh Mécanisme de roulement à courroie et essieu de mécanisme de roulement présentant des mécanismes de roulement à courroie
DE202012101929U1 (de) 2012-05-25 2012-07-17 Impex Forstmaschinen Gmbh Forstwirtschaftliche Arbeitsmaschine
AU2014241527B2 (en) * 2013-03-25 2017-05-04 Polaris Industries Inc. Tracked all-terrain vehicle
GB201311024D0 (en) 2013-06-20 2013-08-07 Agco As Suspension system for a self-propelled harvesting machine with tracks
EP3055195A1 (fr) 2013-10-11 2016-08-17 Franz Aunkofer Véhicule auxiliaire agricole non entraîné, procédé permettant son utilisation pour des transports de charges agricoles et ensemble de traction agricole
DE102013220570A1 (de) 2013-10-11 2015-04-16 Franz Aunkofer Antriebsloses landwirtschaftliches hilfsfahrzeug, verfahren zu dessen einsatz bei landwirtschaftlichen lastentransporten sowie landwirtschaftlicher zugverbund
DE102014208070A1 (de) 2014-04-29 2015-12-17 Deere & Company Die Fahrzeugdynamik berücksichtigendes Kontrollsystem zur Positionssteuerung eines Geräts für ein landwirtschaftliches Arbeitsfahrzeug
RU2615828C2 (ru) * 2015-07-29 2017-04-11 Михаил Дмитриевич Косткин Система подвески и подвеска движителя вездехода
IT201600081200A1 (it) * 2016-08-02 2018-02-02 Cnh Ind Italia Spa Sistema di cingolo per veicolo da lavoro
US10730551B2 (en) 2016-08-09 2020-08-04 Polaris Industries Inc. Tracked all-terrain vehicle
DE102017214354B3 (de) 2017-04-24 2018-09-27 Deere & Company Landwirtschaftliches Arbeitsfahrzeug mit Bodeneingriffsmitteln zur Übertragung von Querkräften
US11753093B2 (en) 2019-04-09 2023-09-12 Cnh Industrial America Llc Suspension system for a track-driven work vehicle with pivoting roller wheel assemblies
US11618515B2 (en) 2019-04-09 2023-04-04 Cnh Industrial America Llc Suspension system for a track-driven work vehicle with tandem rear idler/roller
US12403965B2 (en) 2020-01-23 2025-09-02 Soucy International Inc. Multi-member frame assembly for a track system
EP4093655A4 (fr) 2020-01-23 2024-03-06 Soucy International Inc. Ensemble châssis suspendu pour système de chenille
US11964710B2 (en) * 2020-01-27 2024-04-23 Ricoh Company, Ltd. Crawler type traveling body and traveling apparatus
CA3131066A1 (fr) 2020-09-18 2022-03-18 Soucy International Inc. Structure de support pour raccorder au moins un assemblage de roue de support a un chassis d'un systeme de piste et systeme de piste comprenant la structure
CA3131209A1 (fr) 2020-09-18 2022-03-18 Soucy International Inc. Structure de support pour raccorder au moins un assemblage de roue de support a un element de chassis d'un systeme de piste et systeme de piste comprenant la structure

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US7520575B2 (en) * 2007-06-29 2009-04-21 Agco Corporation Tension management system for an endless track of a work machine
US20090001809A1 (en) * 2007-06-29 2009-01-01 Agco Corporation Tension management system for an endless track of a work machine
US11186330B2 (en) 2010-06-30 2021-11-30 Camso Inc. Track assembly for an off-road vehicle
US10272959B2 (en) * 2010-06-30 2019-04-30 Camso Inc. Track assembly for an off-road vehicle
US9033431B1 (en) 2010-06-30 2015-05-19 Camoplast Solideal Inc Track assembly for an off-road vehicle
US20120023881A1 (en) * 2010-07-30 2012-02-02 Dirk Speckamp Self-propelled harvesting machine
US8341926B2 (en) * 2010-07-30 2013-01-01 Claas Selbstfahrende Erntemaschinen Gmbh Self-propelled harvesting machine with hydropneumatic dampening system
US10933877B2 (en) 2010-12-14 2021-03-02 Camso Inc. Track drive mode management system and methods
US9290216B2 (en) * 2011-04-13 2016-03-22 Bpg Recreational Inc. Suspension assembly for personal tracked vehicle
US20140138169A1 (en) * 2011-04-13 2014-05-22 Ryan James Fairhead Suspension assembly for personal tracked vehicle
US11661125B2 (en) 2011-06-13 2023-05-30 Camso Inc. Track assembly for traction of an off-road vehicle
US9505454B1 (en) 2011-06-13 2016-11-29 Camso Inc. Track assembly for traction of an off-road vehicle
US10399619B1 (en) 2011-06-13 2019-09-03 Camso Inc. Track assembly for traction of an off-road vehicle
US10112663B1 (en) 2011-06-13 2018-10-30 Camso Inc. Track assembly for traction of an off-road vehicle
US20150097361A1 (en) * 2012-06-27 2015-04-09 Louis-Philippe Rivard Mobile stabilisation device
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US20140265198A1 (en) * 2013-03-15 2014-09-18 Kuhn North America, Inc. Bogie axle for a machine
US9149000B2 (en) * 2013-03-15 2015-10-06 Kuhn North America, Inc. Bogie axle for a machine
US10246148B2 (en) 2014-04-25 2019-04-02 Ponsse Oyj Crawler-track unit, forest machine and forest machine assembly
US11897558B2 (en) 2015-03-04 2024-02-13 Camso Inc. Track system for traction of a vehicle
US11167810B2 (en) 2015-03-04 2021-11-09 Camso Inc. Track system for traction of a vehicle
US11046377B2 (en) 2015-03-04 2021-06-29 Camso Inc. Track system for traction of a vehicle
US10783723B2 (en) 2015-06-29 2020-09-22 Camso Inc. Systems and methods for monitoring a track system for traction of a vehicle
US12008846B2 (en) 2015-06-29 2024-06-11 Camso Inc. Systems and methods for monitoring a track system for traction of a vehicle
US10875591B2 (en) * 2015-08-04 2020-12-29 Camso Inc. Track system for traction of an agricultural vehicle travelling on fields and roads
US20170036714A1 (en) * 2015-08-04 2017-02-09 Camso Inc. Track system for traction of an agricultural vehicle travelling on fields and roads
US11077897B2 (en) 2015-10-23 2021-08-03 Camso Manufacturing Italy S.R.L. Track system for traction of a vehicle
US20190127104A1 (en) * 2017-11-02 2019-05-02 Krones Ag Glue supply for labeling unit with glue printer
US10703524B2 (en) * 2017-11-02 2020-07-07 Krones Ag Glue supply for labeling unit with glue printer
EP3483048A1 (fr) * 2017-11-08 2019-05-15 CLAAS Industrietechnik GmbH Mécanisme de déplacement sur chenille pour un engin agricole
RU2765588C2 (ru) * 2017-11-08 2022-02-01 КЛААС ИНДУСТРИТЕХНИК ГмбХ Гусеничная ходовая часть для сельскохозяйственной рабочей машины
US11046375B2 (en) 2017-11-08 2021-06-29 Claas Industrietechnik Gmbh Track roller unit for an agricultural working machine
US11835955B2 (en) 2017-12-08 2023-12-05 Camso Inc. Systems and methods for monitoring off-road vehicles
EP3556579B1 (fr) * 2018-04-19 2022-02-09 NAF Neunkirchener Achsenfabrik AG Bogie pour un véhicule forestier et véhicule comprenant au moins un essieu de bogie
US11225118B2 (en) 2018-04-19 2022-01-18 Naf Neunkirchener Achsenfabrik Ag Bogie for a forestry vehicle and vehicle with at least one bogie axle
US12090795B2 (en) 2018-08-30 2024-09-17 Camso Inc. Systems and methods for monitoring vehicles with tires
US12254616B2 (en) 2018-08-30 2025-03-18 Camso Inc. Systems and methods for monitoring tracked vehicles
US20210269106A1 (en) * 2020-02-27 2021-09-02 Claas Industrietechnik Gmbh Track drive of an agricultural production machine
US12017710B2 (en) * 2020-02-27 2024-06-25 Claas Industrietechnik Gmbh Track drive of an agricultural production machine
USD1054458S1 (en) * 2022-01-13 2024-12-17 Soucy International Inc. Track assembly
USD1072887S1 (en) 2022-01-13 2025-04-29 Soucy International Inc. Track assembly
USD1072888S1 (en) 2022-01-13 2025-04-29 Soucy International Inc. Track assembly
USD1090642S1 (en) 2022-01-13 2025-08-26 Soucy International Inc. Track assembly

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EP1776268A1 (fr) 2007-04-25
CA2576984A1 (fr) 2006-02-23
EP1776268B1 (fr) 2011-01-12
WO2006018215A1 (fr) 2006-02-23
US20100071969A1 (en) 2010-03-25
US8147007B2 (en) 2012-04-03
CA2576984C (fr) 2012-01-17

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