A gearbox for a gas turbine engine includes a housing that includes first and second housing portions interconnected by an intermediate housing portion to provide a generally U-shaped structure. Each of the first and second housing portions includes opposing first and second faces. The second faces of the first and second housing portions are adjacent to one another. First and second gear sets are respectively arranged in the first and second housing portions. A third gear set is arranged in the intermediate portion and is coupled to the first and second gear sets. Accessory drive component mounts are provided on at least three of the first and second faces of the first and second housing portions. The mounts are each configured to support an accessory drive component coupled to one of the first and second gear sets.

Gearbox for gas turbine engine

A mulching mower is provided for mowing and mulching turf vegetation in order to reduce the size of the cut vegetation and more evenly distribute the vegetation once thus cut. Counterrotating, coaxial blade and mulching tool assemblies are provided. Each blade assembly is driven by a central shaft rotatably mounted through a drive barrel which drives the mulching tool. A belt drive assembly translates rotation at a driving sheave into rotation in two different directions at spindles positioned along the mower, each spindle including a blade and a mulching tool.

Counterrotation mulching mower

A mulching mower is provided for mowing and mulching turf vegetation in order to reduce the size of the cut vegetation and more evenly distribute the vegetation once thus cut. Counterrotating, coaxial mowing blade and mulching tool assemblies are provided. The mowing blade assembly is driven by a central shaft rotatably mounted through a drive barrel which drives the mulching tool. The mulching tool assembly includes a plurality of blades, typically pivotally mounted, at least one of the mulching blades being in a lower mulching plane, and at least one other of the mulching blades being in an upper mulching plane.

Counterrotation mulching mower and blade assembly

A disc mower-conditioner having the disc cutterbar (30) driven at each end thereof, the rotational power being delivered to the outboard end of the disc cutterbar (30) by a power transfer mechanism (28) disposed above the disc cutterbar (30), is disclosed wherein a drive mechanism (20) includes a gearbox (23) operable to receive rotational power from a power input shaft (22) and transfer rotational power to three output shafts (24,26,34) to power equally the opposing ends of the disc cutterbar (30) and to power the rotation of a conditioning mechanism (32,33) positioned rearwardly thereof. The gearbox (23) is provided with a removable lid (60) rotatably supporting one output shaft (26) operably associated with the power transfer mechanism (28) to deliver rotational power to the outboard end of the disc cutterbar (30).

Split cutterbar drive mechanism

A rotary cutter apparatus is provided for shredding vegetation in order to generally reduce the size of cut vegetation and more evenly distribute the vegetation once thus cut. Counterrotating, coaxial blade assemblies are provided. A multiple gear drive shaft has one drive gear for engaging and driving one blade assembly and another drive gear for engaging and driving the other blade assembly. The multiple gear drive shaft also has an interchangeability characteristic which determines the respective rotational directions of the counterrotating blade assemblies. Enhanced gear and bearing lubrication is also achieved.

Rotary cutter with reversible counterrotation gearbox

A high-speed bevel gear transmission system for transmitting power from an input shaft to a pair of parallel outputs shafts the axes of which intersect each other. The input shaft has a pair of driving bevel gears which are fixedly mounted thereon such that the driving bevel gears face in opposite directions and which have the same number and size of teeth spirally arranged in the opposite directions each other. The output shafts are supported on angular contact ball bearings and have two driven bevel gears fixedly mounted thereon which are engaged with the driving bevel gears. The speed transmission ratio of the output shafts to the input shaft is 1.45:1 to 0.476:0.1, the relation between a pressure angle α and helix angle β of the driving bevel gears and driven bevel gears, and a pitch cone angle δ of the driven bevel gears are defined by the formula, R=[(tanα·sin δ)/cos β]-tanβ· cos δ when 0.324≦R≦0.1.

High-speed bevel gear transmission system

PURPOSE:To transmit a large power with a comparatively small bevel gear by setting a speed transmitting ratio to output shafts against an input shaft, a pressure angle between a driving bevel gear and a driven bevel gear, and an angle of torsion to be fixed values. CONSTITUTION:A speed transmitting ratio between bevel gears 6, 7 and bevel gears 16, 17, that is, a speed transmitting ratio to output shafts 10, 11 against an input shaft 2, is set to be 1.45-1/2.1. Also, an angle pressure alpha on teeth of the bevel gears 6, 7, 16, 17, an angle of torsion beta of teeth of the bevel gears 6, 7, 16, 17, and a pitch cone angle delta of the bevel gears 16, 17 are set to be within a range that is set by an equation, -0.324<=tanalpha.sindelta/cosbeta-tanbeta.cosdelta<=0.1.

High speed geared transmission

PURPOSE:To provide a bevel bear reduction gearing device which can eliminate the thrust bearing of a small bevel gear and make the thrust load of a large bevel gear zero or minimum. CONSTITUTION:This reduction gearing device has bevel gears 11, 12 of reverse spiral direction to each other engaged with a shaft back to back, large bevel gears 13, 14 engaged respectively with shafts 22, 23 and also engaged with the gears 11, 12 respectively, and bearings 15 - 18, 15' to 18' engaged with the shafts 21 to 23, respectively. Assuming that the conical angle of the gears 13, 14 is represented by delta, pressure angle by alpha and spiral angle by beta, the conical angle delta of the large bevel gear is obtained to satisfy the right formula. Since the two gears 11, 12 incorporate reverse spiral directions of the teeth thereof according to this configuration, their thrust loads Pa1 can cancel to each other so as to eliminate the thrust bearing of the shaft 21. Further, the conical angle beta of the large bevel gears is set in the range capable of satisfying the formula to thereby enable to set the thrust load Pa2 of the large gears 13, 14 extremely small and to accordingly realize acceleration of the bevel gear reducting gearing device.

Tamura Tetsuji

Papers

High-speed bevel gear transmission system

High speed geared transmission

High speed gear reduction gearing device