WO2009101644A1 - Machine agricole motorisée - Google Patents

Machine agricole motorisée Download PDF

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Publication number
WO2009101644A1
WO2009101644A1 PCT/IT2008/000092 IT2008000092W WO2009101644A1 WO 2009101644 A1 WO2009101644 A1 WO 2009101644A1 IT 2008000092 W IT2008000092 W IT 2008000092W WO 2009101644 A1 WO2009101644 A1 WO 2009101644A1
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WO
WIPO (PCT)
Prior art keywords
gear
primary
reverse gear
forward gear
axis
Prior art date
Application number
PCT/IT2008/000092
Other languages
English (en)
Inventor
Luigi Feligioni
Original Assignee
Cge Services & Trading S.R.L.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Cge Services & Trading S.R.L. filed Critical Cge Services & Trading S.R.L.
Priority to PCT/IT2008/000092 priority Critical patent/WO2009101644A1/fr
Publication of WO2009101644A1 publication Critical patent/WO2009101644A1/fr

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Classifications

    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01B—SOIL WORKING IN AGRICULTURE OR FORESTRY; PARTS, DETAILS, OR ACCESSORIES OF AGRICULTURAL MACHINES OR IMPLEMENTS, IN GENERAL
    • A01B33/00—Tilling implements with rotary driven tools, e.g. in combination with fertiliser distributors or seeders, with grubbing chains, with sloping axles, with driven discs
    • A01B33/02—Tilling implements with rotary driven tools, e.g. in combination with fertiliser distributors or seeders, with grubbing chains, with sloping axles, with driven discs with tools on horizontal shaft transverse to direction of travel
    • A01B33/028—Tilling implements with rotary driven tools, e.g. in combination with fertiliser distributors or seeders, with grubbing chains, with sloping axles, with driven discs with tools on horizontal shaft transverse to direction of travel of the walk-behind type
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01B—SOIL WORKING IN AGRICULTURE OR FORESTRY; PARTS, DETAILS, OR ACCESSORIES OF AGRICULTURAL MACHINES OR IMPLEMENTS, IN GENERAL
    • A01B33/00—Tilling implements with rotary driven tools, e.g. in combination with fertiliser distributors or seeders, with grubbing chains, with sloping axles, with driven discs
    • A01B33/08—Tools; Details, e.g. adaptations of transmissions or gearings
    • A01B33/082—Transmissions; Gearings; Power distribution

Definitions

  • the object of the present invention is a motorized agricultural machine for the treatment of an agricultural plot of land, particularly a motor hoe, a walking tractor, or the like.
  • Known motor hoes and walking tractors comprise a plurality of rotary hoes adapted to clear the agricultural plot of land to be treated.
  • Such rotary hoes are mounted on an output shaft that, in use conditions, is approximately parallel to the agricultural plot of land to be treated. More particularly, the output shaft is typically beneath the plot surface in use conditions, so that the hoes operate below the surface.
  • the output shaft is driven by an engine, usually of the endothermic type.
  • a drive is provided between engine and output shaft, which is adapted to reduce the rotation speed and increase the torque, which are provided by the engine at the output shaft.
  • the drive can have a single gear, particularly forward gear or, alternatively, two gears, particularly forward and reverse gears .
  • different solutions can be provided for the drive.
  • the engine is of the so-called "horizontal axis" type, i.e. it is an engine adapted to operate with the engine shaft thereof essentially orthogonal to the force of gravity, and parallel to plot of land and output shaft in the agricultural machine standard use conditions.
  • the drive is provided with a plurality of belt pulleys rotating around rotation axes which are parallel to engine shaft and output shaft .
  • the engine is of the so-called "vertical axis" type, that is, it is adapted to operate with the engine shaft thereof approximately parallel to the force of gravity and essentially orthogonal to the plot of land in the agricultural machine standard use conditions.
  • the drive comprises a plurality of belt pulleys rotating around a rotation axes parallel to the engine axis and orthogonal to the plot of land.
  • the drive also comprises a worm screw, also parallel to the engine shaft, which is driven by one of the above-mentioned pulleys and which meshes a gear wheel rotatable around a rotation axis oriented orthogonally to the engine axis. Such gear wheel operates in turn the output shaft .
  • Horizontal axis engines have considerable costs, higher than those of vertical axis engines, which therefore are preferred over horizontal axis engines. However, the latter require using drives with low efficiencies, mainly as a result of the presence of the gear wheel-worm screw mating.
  • the object of the present invention is to provide an agricultural machine which at least partially overcomes the drawbacks cited with reference to the prior art .
  • the object of the present invention is to provide an agricultural machine, provided both with forward gear and with reverse gear, which has a sufficiently reduced constructive complexity, and which is capable of ensuring sufficiently high energy efficiencies .
  • a motorized agricultural machine comprising:
  • a drive for the operative connection of engine shaft with output shaft which is configurable at least according to one forward gear and one reverse gear configurations, in which such drive comprises a forward gear primary member and a reverse gear primary member which can be simultaneously driven by engine shaft, and respectively suitable to cause opposite rotations of the output shaft following rotations according to the same direction of the engine shaft, in which forward gear and reverse gear primary members are rotatable around a forward gear primary axis and a reverse gear primary axis, respectively, which are skew or incident relative to the engine axis.
  • FIG. 1 is a schematic side view of a motorized agricultural machine according to the invention
  • FIG. 2 is a schematic side view partially in phantom of the motorized agricultural machine in Fig. 1;
  • Fig. 3 is a schematic side partially in phantom of a portion of the motorized agricultural machine of Fig. 1 according to a possible embodiment of the invention;
  • Fig. 4 is a schematic side view partially in phantom of the motorized agricultural machine portion of Fig. 3 according to a further embodiment of the invention
  • Fig. 5 is a schematic perspective partial view of the motorized agricultural machine portion of Fig. 4
  • Fig. 6 is a schematic partially sectional side view according to the arrow A of a further portion of the motorized agricultural machine of Fig. 1
  • Fig. 7 is a schematic sectional view of a component of the motorized agricultural machine of Fig. 1
  • Fig. 8 is a schematic sectional view of a further component of the motorized agricultural machine of Fig. 1
  • Fig. 9 is a schematic sectional view of a further component of the motorized agricultural machine of Fig.
  • Fig. 10 is a schematic sectional view of a further component of the agricultural machine of Fig. 1;
  • Fig. 11 is a schematic sectional view of a further component of the motorized agricultural machine of Fig. l;
  • Fig. 12 is a schematic sectional view of a further component of the motorized agricultural machine of Fig. 1;
  • Fig. 13 is a schematic perspective view of a portion of the motorized agricultural machine of Fig. 1 according to a further possible embodiment of the invention.
  • a motorized agricultural machine to work an agricultural plot of land 35 is generally designated with the reference numeral 1.
  • the agricultural machine 1 comprises an output shaft 2 which is capable of rotating according to an output axis U, and which is able to support one or more tools 3 suitable to operate on the agricultural plot of land 35.
  • tools 3 can comprise hoes 3' which are either connected or connectable to the output shaft 2 capable of clearing the agricultural plot of land 35 upon the action of the output shaft 2 rotation.
  • the hoes 3' preferably operate at least partially beneath the plot surface to be worked, and are caused to rotate so as to turn the plot of land over and clear it.
  • Such land clearing operation is promoted by the presence of a resistance against the feed of the agricultural machine 1, which can be achieved, for example, by means of a resistance beak 4 intended to dig in the agricultural plot of land 35 during the land clearing operation.
  • a resistance against the feed of the agricultural machine 1 which can be achieved, for example, by means of a resistance beak 4 intended to dig in the agricultural plot of land 35 during the land clearing operation.
  • the output shaft 2 output axis U With reference to a working plane P defined by the plot of land 35 to be worked, the output shaft 2 output axis U, in use conditions of the agricultural machine 1, is advantageously arranged approximately parallel to such working plane P, or approximately lying thereon.
  • the agricultural machine 1 can comprise a handlebar 5, for example, provided on the two sides thereof with two handles 6 suitable to be gripped by the same user.
  • the agricultural machine 1 comprises an engine 7 provided with engine shaft 8 capable of rotating according to an engine axis M, and operatively connected to the output shaft 2 (Figs. 2-4) .
  • the engine 7 is preferably an endothermic engine of the so-called "vertical axis" type, that is an engine so shaped as to optimally operate when the engine axis M thereof is approximately parallel to the acceleration of gravity G.
  • the engine axis M is arranged transversally, preferably orthogonally, to the working plane P defined by the plot of land to be worked 35 in the agricultural machine standard use conditions.
  • the vertical axis engines are particularly advantageous, since they combine high performance to sufficiently low costs .
  • the agricultural machine 1 comprises a drive 9, particularly a drive suitable to perform an angular speed reduction and an intensification of the driving torque from engine shaft 8 to output shaft 2.
  • the drive 9 is preferably housed within a holding box 10, that can be, for example, opened for the maintenance operations, and is supported by a support main structure 11.
  • the drive 9 is preferably arranged beneath the engine 7, so that the engine shaft 8 enters the drive 10 passing through the holding box 11 from the top.
  • the drive 9 is configurable according to at least one forward and one reverse gears.
  • the forward gear is adapted to the agricultural machine 1 operation, when the latter has to perform the working operations on the agricultural plot of land 35.
  • output shaft 2 and hoes 3' rotate according to a direction suitable to urge the agricultural machine feed (with reference to the Figs. 1 and 2, when the forward gear is engaged, the engine 7 rotates output shaft 2 and rotary hoes 3' counter-clockwise according to the arrow F7) .
  • the reverse gear is suitable to cause a rotation of hoes 3' and engine shaft 2 opposite the forward gear rotation (with reference to the Figs. 1 and 2, when the reverse gear is engaged, hoes 3' and output shaft 2 rotate clockwise, according to the arrow F8) .
  • one or more levers 12 can be provided, preferably one for each gear, for example arranged on the handlebar 5 two opposite sides (in the Figs. 1 and 2, only one of such levers 12 is visible) .
  • Each of the levers 12 is connected or connectable to the drive 9 for the engage of the desired gear, for example by means of connecting cables 13 acting on the drive 9 according to modes which will be described herein below.
  • the drive 9 comprises a forward gear primary member 14 and a reverse gear primary member 15, respectively rotating around a forward gear primary axis MF and a reverse gear primary axis MR.
  • the forward gear 14 and reverse gear 15 primary members are simultaneously actuatable by the engine shaft 8.
  • the forward gear 14 and reverse gear 15 primary members are connected to the engine shaft 8 in such a manner that, for rotations according to the same direction of engine shaft 8, they perform rotations which are suitable to cause opposite rotations of the output shaft 2.
  • the forward gear primary member 14 is connected to the output shaft 2 so that the rotations thereof, upon the action of the engine shaft 8 rotation, cause forward gear rotations in the output shaft 2 (counter-clockwise direction, arrow F7 in the Figs. 1 and 2) .
  • the reverse gear primary member 15 is connected to the output shaft 2 so that the rotations thereof, upon the action of an engine shaft 8 rotation according to the same direction necessary for the forward gear, cause reverse gear rotations in the output shaft 2 (clockwise direction, arrow F8 in the Figs. 1 and 2) .
  • the configuration described above is particularly advantageous, since it permits to exploit conventional endothermic vertical axis engines, capable of rotating according to a single rotation direction (for example, engines of the type used in the lawnmowers) .
  • forward gear main member 14 and reverse gear main member 15 can be simultaneously driven by engine shaft 8.
  • the engine activation makes so that both forward gear main member 14 and reverse gear main member 15 concomitantly rotate according to directions which would per se cause opposite rotations of the output shaft 2.
  • the drive 2 is advantageously shaped such as to selectively implement either the operative connection between forward gear primary member 14 and output shaft 2, or between reverse gear primary member 15 and output shaft 2.
  • forward gear 14 and reverse gear 15 primary members, engine shaft 8, and output shaft 2 are arranged according to determined spatial orientations.
  • engine shaft 8 engine axis M and output shaft 2 output axis U are mutually skew or incident.
  • forward gear MF and reverse gear MR primary axes are skew or incident relative to engine axis M.
  • skew and incident are to be intended in the geometrical meaning thereof. Particularly, with the term “skew axes”, two axes are meant that are nor incident nor parallel, and that, therefore, are not coplanar.
  • the engine M, output U, forward gear primary MF, and reverse gear primary MR axes define fictitious planes which are orthogonal thereto (Fig. 5) .
  • engine axis M defines an engine plane PM
  • output axis U defines an output plane PU
  • forward gear primary axis MF defines a forward gear primary plane PMF
  • reverse gear primary axis MR defines a reverse gear primary plane PMR.
  • the engine plane PM is advantageously transversal to the output plane PU.
  • forward gear primary plane PMF and reverse gear primary plane PMR are transversal to the engine plane PM.
  • the forward gear PMF and reverse gear PMR primary planes are preferably orthogonal to the engine plane PM. In this manner, advantageously, the forward gear MF and reverse gear MR primary axes are mutually essentially parallel or essentially coincident .
  • the engine plane PM is essentially orthogonal to the output plane PU.
  • the forward gear primary member 14 comprises a forward gear primary pulley 14'
  • the reverse gear primary member 15 comprises a reverse gear primary pulley 15' .
  • Forward gear primary pulley 14' and reverse gear primary pulley 15' are rotatable around forward gear primary axis MF and reverse gear primary axis MR, respectively.
  • the forward gear MF and reverse gear MR primary axes are preferably mutually coincident or parallel.
  • forward gear primary pulley 14' and reverse gear primary pulley 15' are arranged one facing the other.
  • Forward gear 14' and reverse gear 15' primary pulleys are connected by a primary belt 16 common to a driving pulley 17 associated with the engine shaft 8.
  • the driving pulley 17 is preferably mounted directly on the engine shaft 8 at one end thereof.
  • the driving pulley 17 (of which a possible embodiment is illustrated in Fig. 7) can be axially constrained to the engine shaft 8 by means of a threaded connection member to be inserted in a corresponding threaded seat of the engine shaft 8 end (not shown in the Figures) , and it can be made rotatably integral to the latter by means of a shape connection achievable, for example, through a key- key seat mating.
  • the engine axis M around which also the driving pulley 17 is rotatable, preferably passes through an inner space 18 of the drive 9 which is defined by the forward gear 14' and reverse gear 15' primary pulleys (Fig. 5) .
  • the engine plane PM is essentially orthogonal to the forward gear PMF and reverse gear PMR primary planes.
  • the primary belt 16 can be selected from those that are usually used in the belt drives, for example between belts of the flat, trapezoidal section, geared, or grooved types.
  • the primary belt 16 can be selected from the group consisting of cables, wires, or the like.
  • driving pulley 17 rotates in a plane (engine plane PM) that is transversal to those in which forward gear primary pulley 14' and reverse gear primary pulley 15' rotate (forward gear PMF and reverse gear PMR primary- planes)
  • the driving belt 17 undergoes torsions upon passing between driving pulley 17 and forward gear primary pulley 14', and between driving pulley 17 and reverse gear primary pulley 15' .
  • the use of conventional belts that are capable of twisting without breaking, is therefore particularly advantageous.
  • the drive 9 advantageously comprises an idle tensioning pulley 19 (a possible embodiment of which is illustrated in Fig. 8) .
  • the tensioning pulley 19 is preferably connected to the support main structure 11, and it can freely rotate around an idle axis AF.
  • the idle axis AF can be optionally moved in such a manner as to change the tensioning pulley 19 distance relative to the forward gear 14' and reverse gear 15' primary pulleys, so as to change the primary belt 16 tension.
  • the tensioning pulley 19 is preferably arranged in the drive 9 inner space 18.
  • idle axis AF is transversal to engine axis M (Figs. 2 and 3) .
  • idle axis AF is essentially parallel to engine axis M (Fig. 4) .
  • the drive portions comprised between engine shaft 8, and forward gear 14 and reverse gear 15 primary members, respectively, are preferably so shaped as to implement an angular speed reduction.
  • driving pulley 17, forward gear primary pulley 14', and reverse gear primary pulley 15' have diameters such that the reduction ratios between driving pulley 17, and forward gear primary pulley 14' and reverse gear primary pulley 15', respectively, are comprised between 1/4 and 1/2, and which are preferably of about 1/2.7.
  • the forward gear primary member 14 advantageously comprises a forward gear auxiliary pulley 20, and the reverse gear primary member 15 comprises a reverse gear auxiliary pulley 21 (Figs. 5, 9, 10) .
  • Forward gear auxiliary pulley 20 is rotatable around forward gear primary axis MF, integrally to forward gear primary pulley 14'
  • reverse gear auxiliary pulley 21 is rotatable around reverse gear primary axis MR, integrally to reverse gear primary pulley 15'.
  • the forward gear primary 14' and auxiliary 20 pulleys are preferably manufactured in a single piece (Fig. 10) .
  • the reverse gear primary 15' and auxiliary 21 pulleys are also preferably manufactured in a single piece (Fig. 9) .
  • the forward gear 14' and reverse gear 15' primary pulleys respectively translate in rotations with the same angular speeds of the forward gear 20 and reverse gear 21 auxiliary pulleys.
  • the forward gear 14' and reverse gear 15' primary pulleys preferably have diameters higher than the diameters of forward gear 20 and reverse gear 21 auxiliary pulleys, respectively, so that, while keeping the angular speed constant, the peripheral speeds of the auxiliary pulleys are below those of the corresponding primary pulleys .
  • the forward gear auxiliary pulley 20 is advantageously connected to a forward gear driven pulley 22 through a forward gear auxiliary belt 24, and the reverse gear auxiliary pulley 21 is connected to a reverse gear driven pulley 23 through a reverse gear auxiliary belt 25 (Fig. 5) .
  • the forward gear 22 and reverse gear 23 driven pulleys are preferably rotatable integrally one to the other around a same driven axis C.
  • the forward gear 22 and reverse gear 23 driven pulleys can be mounted on a common driven shaft 26 (Fig. 6) that is rotatable around the driven axis C.
  • the driven axis C is essentially parallel to the forward gear primary axis MF and/or the reverse gear primary axis MR, and preferably parallel to both. Still more preferably, the driven axis C is essentially parallel to the output axis U.
  • the connection of forward gear driven pulley 22 to forward gear auxiliary pulley 20 through forward gear auxiliary belt 24, and the connection of reverse gear driven pulley 23 to reverse gear auxiliary pulley 21 through reverse gear auxiliary belt 25 make that the forward gear 22 and reverse gear 23 driven pulleys, when the engine 7 is driven, are caused to perform mutually opposite rotations around the driven axis C. Consequently, if the forward gear 22 and reverse gear 23 driven pulleys were concomitantly driven, they would tend to twist the driven shaft 26 which they are integrally connected upon rotating.
  • the drive 9 advantageously comprises selective tensioning means 27 adapted to tension one or the other of forward gear auxiliary belt 24 and reverse gear auxiliary belt 25 (shown in Fig. 2, not shown in Fig. 5, for example) .
  • the selective tensioning means 27 comprise a forward gear tightening pulley 28, capable of tensioning the forward gear auxiliary belt 24, and a reverse gear tightening pulley 29, capable of tensioning the reverse gear auxiliary belt 25.
  • the forward gear 24 and reverse gear 25 auxiliary belts are mounted loose, that is, not tensioned or, anyhow, not much tensioned, on the forward gear auxiliary 20 and driven 22 pulleys, and on the reverse gear auxiliary 21 and driven 23 pulleys, respectively.
  • the rotations of forward gear 20 and reverse gear 21 auxiliary pulleys are not capable of inducing the rotations of forward gear 22 and reverse gear 23 driven pulleys, respectively, since the forward gear 24 and reverse gear 25 auxiliary belts slide thereon.
  • the forward gear auxiliary belt 24 or the reverse gear auxiliary belt 25 are tensioned, respectively. In this manner, the forward or the reverse gears is consequently engaged.
  • the forward gear tightening pulley 28 pushes on the forward gear auxiliary belt 24 preferably, but not necessarily, bottom-up.
  • the reverse gear tightening pulley 29 pushes on the reverse gear auxiliary belt 25 preferably, but not necessarily, top-down.
  • the forward gear 28 and reverse gear 29 tightening pulleys are actuatable by the user by means of levers 12 that are arranged on the agricultural machine 1 handlebar 5, which are connected to the tightening pulleys through connecting cables 13, described above.
  • the tightening pulleys which are preferably rotatably connected to the support main structure 11, are rotated, for example, upon a connecting cables 13 traction action.
  • the forward gear 28 and reverse gear 29 tightening pulleys preferably comprise a main plate to which a rotatable member suitable to push on the belts, for example, of the wheel, or pulley type, is hinged.
  • the forward gear 24 and reverse gear 25 auxiliary belts can be selected, such as the primary belt 16, from the belts which are typically used in the belt drives. Alternatively, they can be selected from the group consisting of cables, wires, or the like.
  • the drive portion comprised between forward gear primary member 14 and forward gear driven pulley 22, and the drive portion comprised between reverse gear primary member 15 and reverse gear driven pulley 23, are so shaped as to implement further angular speed reductions.
  • forward gear auxiliary pulley 20 and forward gear driven pulley 22 advantageously have diameters such as to implement a reduction ratio ranging between 1/4 and 1/2, preferably of about 1/2.6.
  • reverse gear auxiliary pulley 21 and reverse gear driven pulley 23 have diameters such as to implement a reduction ratio ranging between 1/7 and 1/4, preferably of about 1/5.6.
  • the drive 9 further comprises an auxiliary reducer 32 operatively arranged between the forward gear 22 and reverse gear 23 driven pulleys and output shaft 2, preferably a reducer of the chain type (see, for example, Fig. 6) .
  • a rack 33 can be formed or mounted on the driven shaft 26, which is adapted to be connected to a chain which, in turn, can be connected to a further rack
  • the auxiliary reducer 32 is preferably shaped so as to implement an angular speed reduction ratio ranging between 1/4 and 1/6, still more preferably of about 1/4.8.
  • the drive 9 implements an angular speed reduction preferably ranging between 1/64 and 1/24, still more preferably of about 1/35 between engine shaft 8 and output shaft 2, when it is shaped according to the forward gear configuration, and an angular speed reduction preferably ranging between and between 1/48 and 1/112, still more preferably of about 1/73, when it is shaped according to the reverse gear configuration.
  • engine shaft 8 and driving pulley 17 begin to rotate around engine axis M with a predefined rotation direction, for example the one illustrated with the arrow Fl in Fig. 5.
  • a predefined rotation direction for example the one illustrated with the arrow Fl in Fig. 5.
  • forward gear primary pulley 14' and reverse gear primary pulley 15' are caused to rotate around the forward gear MF and reverse gear RF primary axes, respectively, according to opposite directions, respectively indicated by the arrows F2 and F3 in Fig. 5.
  • the idle tensioning pulley 19 is caused to rotate around the idle axis AF according to a direction indicated by the arrow F4 in Fig . 5.
  • the forward gear 20 and reverse gear 25 auxiliary pulleys are also made to rotate around the forward gear MF and reverse gear RF primary axes, respectively, according to opposite directions indicated by the arrows F2 and F3, respectively, in Fig. 5 (which are the same rotation directions of the forward gear 14' and reverse gear 15' primary pulleys) .
  • reverse gear driven pulley 23 and driven shaft 26 rotate. Since in such configuration reverse gear auxiliary pulley 21 and reverse gear driven pulley 23 rotate according to opposite directions, indicated by the arrows F3 and F5, respectively, in Fig. 5, the reverse gear auxiliary belt 25 slides relative to the reverse gear driven pulley 23. [0078] By releasing the forward gear tightening pulley 28 and actuating the reverse gear tightening pulley 29, the reverse gear auxiliary belt 25 is tensioned, consequently an operative connection is created between reverse gear auxiliary pulley 21 and reverse gear driven pulley 23 (reverse gear engage) . The reverse gear driven pulley 23 is caused to rotate around the driven axis C according to the direction indicated by the arrow F6 in Fig.
  • forward gear driven pulley 22 and driven shaft 26 rotate. Since, in such configuration, forward gear auxiliary pulley 20 and forward gear driven pulley 22 rotate according to opposite directions, the directions indicated by the arrows F2 and F6, respectively, in Fig. 5, the forward gear auxiliary belt 24 slides relative to the forward gear driven pulley 22.
  • the agricultural machine When the forward gear is engaged, the output shaft 2, which is connected to the driven shaft 26 through the auxiliary reducer 32, as well as the rotating tools 3 which are mounted on the output shaft, rotate around the output axis U according to the direction indicated by the arrow F7 in Fig. 5. Therefore, the agricultural machine is capable of performing forward movements according to the arrow F in Fig . 2 and 5. [0080] Instead, when the reverse gear is engaged, output shaft 2 and rotating tools 3 rotate around the output axis U according to the direction indicated by the arrow F8 in Fig. 5. The agricultural machine can perform backward movements according to the arrow R in Fig. 2 and 5.
  • the forward gear primary member 14 comprises a forward gear primary gear wheel 14 ' ' which is rotatable around the forward gear primary axis MF
  • the reverse gear primary member 15 comprises a reverse gear primary gear wheel 15'' which is rotatable around the reverse gear primary axis MR (Fig. 13)
  • Forward gear 14'' and reverse gear 15'' primary gear wheels are simultaneously engageable by an engine pinion 34 associated with the engine shaft 8, preferably directly mounted thereon, so as to be also rotatable around engine axis M.
  • the engine pinion 34-forward gear primary gear wheel 14' '-reverse gear primary gear wheel 15'' connection implements a mechanism cinematically equivalent to the driving pulley 17-forward gear primary pulley 14 '-reverse gear primary pulley 15' connection.
  • the forward gear 14'' and reverse gear 15'' primary gear wheels perform rotations which are adapted to trigger the forward gear and reverse gear movements, respectively.
  • forward gear MF and reverse gear MR primary axes are parallel, the forward gear 14'' and reverse gear 15'' primary gear wheels perform opposite rotations following a rotation according to the same direction of the engine pinion 34 (see the arrows Fl,
  • Engine pinion 34, forward gear primary gear wheel 14 ' ' , and reverse gear primary gear wheel 15'' are preferably housed within a holding box
  • forward gear 14 ' ' and reverse gear 15'' primary gear wheels to output shaft 2 can be carried out in accordance with one or more of the embodiments described with reference to the connection of forward gear 14' and reverse gear 15' primary pulleys to output shaft 2.
  • forward gear 20 and reverse gear 21 auxiliary pulleys can be associated, which are in turn connectable to the forward gear 22 and reverse gear 23 driven pulleys by means of the forward gear 24 and reverse gear 25 auxiliary belts.
  • the forward gear 20 and reverse gear 21 auxiliary pulleys can be manufactured in a single piece with the forward gear 14'' and reverse gear 15'' primary gear wheels, respectively.
  • forward gear 20 and reverse gear 21 auxiliary pulleys can be distinguished from and connected to forward gear 14 ' ' and reverse gear 15'' primary gear wheels, for example, by means of pivots 36 and 37, respectively.
  • the auxiliary reducer 32 for example of the chain type, can further be optionally provided between driven shaft 26 and output shaft 2.
  • connection of forward gear 14'' and reverse gear 15'' primary gear wheels to output shaft 2 can be implemented according to different modes, for example, by means of a sequence of gears arranged in series, as an alternative, or in addition to operative connections through belts.
  • a plurality of forward gear and/or reverse gear auxiliary pulleys respectively rotating around the forward gear and reverse gear primary axes, integrally to the forward and backward gear primary members, and respectively connectable to as many forward gear and/or reverse gear driven pulleys through as many forward gear and/or reverse gear auxiliary belts.
  • a plurality of forward and/or backward gears which are actuatable, for example, by tensioning the corresponding auxiliary belts through special tensioning means controllable by the user.
  • the forward gear and reverse gear driven pulleys can be rotatably independent and connected to the output shaft through two separate auxiliary reducers, for example, of the chain type.
  • the rotating tools can comprise wheels that are connected to the output shaft and which are caused to rotate by the latter.

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  • Life Sciences & Earth Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Soil Sciences (AREA)
  • Environmental Sciences (AREA)
  • Power Engineering (AREA)
  • Arrangement Of Transmissions (AREA)

Abstract

L'invention concerne une machine agricole motorisée (1) comprenant: un arbre de sortie (2) pouvant tourner selon un axe de sortie (U) et être associé à un ou à plusieurs outils (3) conçus pour fonctionner sur un terrain agricole (35); un moteur (7) présentant un arbre moteur (8) pouvant tourner selon un axe moteur incident ou oblique (M) par rapport à l'axe de sortie (U), un entraînement (9) pour la liaison fonctionnelle de l'arbre moteur (8) à l'arbre de sortie (2) qui peut être conçu selon une configuration de pignon de marche avant et/ou une configuration de pignon de marche arrière. L'entraînement (9) comprend un élément primaire de pignon de marche avant (14) et un élément primaire de pignon de marche arrière (15) qui peuvent être simultanément actionnés par l'arbre moteur (8) et qui sont respectivement conçus pour faire tourner l'arbre de sortie (2) en sens opposé, suite à une rotation s'effectuant dans un sens identique à celui de l'arbre moteur (8). L'élément primaire de pignon de marche avant (14) et l'élément primaire de pignon de marche arrière (15) peuvent tourner respectivement autour d'un axe primaire de pignon de marche avant (MF) et d'un axe primaire de pignon de marche arrière (MR) qui sont obliques ou incidents par rapport à l'axe de moteur (M).
PCT/IT2008/000092 2008-02-14 2008-02-14 Machine agricole motorisée WO2009101644A1 (fr)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2814600C1 (ru) * 2023-09-05 2024-03-01 Федеральное государственное бюджетное образовательное учреждение высшего образования "Кубанский государственный аграрный университет имени И.Т. Трубилина" Трансмиссия мотоблока

Citations (4)

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RU2814600C1 (ru) * 2023-09-05 2024-03-01 Федеральное государственное бюджетное образовательное учреждение высшего образования "Кубанский государственный аграрный университет имени И.Т. Трубилина" Трансмиссия мотоблока
RU2814599C1 (ru) * 2023-09-05 2024-03-01 Федеральное государственное бюджетное образовательное учреждение высшего образования "Кубанский государственный аграрный университет имени И.Т. Трубилина" Трансмиссия мотокультиватора
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