Abstract: Five receiving holes 2e extending along the axis of a circular cylindrical portion 2b of a housing are formed in the circular cylindrical portion 2b. Those five receiving holes 2e are arranged at equal intervals in the peripheral direction of the circular cylindrical portion 2b. Each receiving hole 2e rotatably receives therein a planetary gear 5. The respective planetary gears 5 are in engagement with an inner gear 3 and a sun gear 4. The teeth of the inner gear 3, the sun gear 4 and the planetary gears 5 are helical teeth. The numbers of teeth of the inner gear 3, the sun gear 4 and the planetary gears 5 are set to 36, 24 and 6, respectively. As a result, the numbers of teeth of the inner gear 3 and the sun gear 4 located between adjacent two planetary gears 5 in the peripheral direction become 7.2 and 4.8, respectively, which are values each having a fraction below the decimal point.

Abstract: A carrier 2 is fixed to one end opening part of a circular cylindrical apparatus main body 1. A plurality of receiving holes 2d, which extend in parallel with a rotation axis L, are formed in the carrier 2 at the same interval in a peripheral direction. A planetary gear 4 is received in each receiving hole 2d such that the planetary gear 4 can rotate on its own axis. An inner gear 5 and a sun gear 9, which are arranged with their axes aligned with the rotation axis L of the apparatus main body 1, are disposed within the apparatus main body 1. The inner gear 5 is engaged with the planetary gears 4 at the outside thereof. The sun gear 9 is engaged with the planetary gears 4 at the inner side thereof. An engagement part between the inner gear 5 and the planetary gear 4 and an engagement part between the sun gear 9 and the planetary gear 4 are displaced from each other in a direction of the rotation axis L so that they are not overlapped with each other in a direction of the rotation axis L.

Abstract: A differential gearing 2 of twin differential type including a center differential unit 14 of planetary gear type and a front differential unit 12 of bevel gear type which are received within a housing 10 is separated from a gear box 6 of a transmission 4, and is disposed within PTO (power transfer off) 8. A common specification can be used for the twin differential unit, and influences by the oil variety can be avoided, assuring a given performance in any application.

Abstract: An internal gear 4 is fitted within a housing 2, and a sun gear 6 is disposed inside the internal gear in concentric relationship therewith. A plurality of planet gears 8 are carried by a planetary carrier 10 connected to the housing 2 and are in meshing engagement with the internal gear 4 and the sun gear 6. Washers 16, 18, 20, 22 and 24 are disposed in regions where the members 2, 4, 6, 8 and 10 slide against respectively. Hollow shafts are connected to a coupling 14 which is connected to the inner periphery of the internal gear 4 and to the inner periphery of the sun gear 6, and a drive from an engine which is input to the housing 2 is delivered through the both shafts. A lubricant oil is introduced through the shaft to lubricate sliding parts which are disposed radially outward of the shaft. A perfect lubrication of the interior of the differential gearing is achieved, seizure resistance can be improved and the occurrence of noises can be reduced.

Abstract: A receiving portion 2e for rotatably receiving therein a planetary gear 3, is formed between a plurality of retaining protrusions 2d of a carrier. A connection portion 2f extending annularly about a rotation axis L is formed on an outer peripheral of a distal end portion of each retaining protrusion 2d. Through this connection portion 2f, the distal end portions of the respective retaining protrusions 2d are connected to each other. Owing to this arrangement, each retaining protrusion 2d is reinforced to minimize its deformation. As a result, deformation of the receiving portion 2e is greatly reduced and the planetary gear 3 receiving in the receiving portion 2e can rotate smoothly.

Abstract: An internal gear 10 is rotatably received within a housing 8 (planetary carrier 2 and case 4), and a sun gear 12 is rotatably disposed on a circle located inside of and concentric with the internal gear 10. Planet gears 14 which are carried within carrying openings 2c formed in a planetary carrier 2 are disposed between the internal gear 10 and the sun gear 12 in meshing engagement with the internal gear 10 and the sun gear 12. The internal gear 10, the sun gear 12 and the planet gears 14 each have spherical gear teeth, and develops a thrust upon occurrence of a relative rotation therebetween. A coupling 16 is connected to the inner periphery of the internal gear 10 through helical splines 10d and 16a for purpose of power transmission. The helical splines provide a novel thrust generating mechanism, which enlarges the extent in which a bias ratio can be adjusted.

Abstract: An interaxle transfer case distributes drive power from an input drive shaft to both a rear propshaft aligned with the input drive shaft and to a front propshaft that is offset from both the input drive shaft and the rear propshaft. Within the transfer case, a planetary gear unit provides for delivering drive power from the input drive shaft to the front and rear propshafts at different speed ratios. A single-pinion differential gear unit within the transfer case provides for unequally dividing drive torque between the front and rear propshafts. Planet gears of the planetary gear unit and pinion gears from the single-pinion differential gear unit are mounted for rotation within a common carrier. The common carrier has one or more extended portions for supporting ends of a transfer case housing.

Abstract: A planetary gear mechanism 3 is provided at one end portion of a housing 2 in a direction of the rotation axis L. The mechanism 3 includes a planetary gear 31 disposed at the housing such that the planetary gear is rotatable about its own axis and revolvable about the rotation axis together with the housing, and an inner gear 33 and a sun gear 34 which are in mesh with the planetary gear. A differential gear mechanism 4 is provided at the other end portion of the housing. The mechanism 4 includes a casing 41 non-rotatably connected to the sun gear, a pair of pinion gears 43 disposed within the casing such that the pinion gears are rotatable about their axes and revolvable about the rotation axis together with the casing, and a pair of side gears 44, which are in mesh with the pinion gears.

Abstract: A planetary gear 5 is contacted at its at least one tooth of all its teeth 51n with an end edge 23d facing an inner releasing part 23c of an inner peripheral surface of a receiving hole 23a irrespective of a rotational position of the planetary gear 5. By doing so, the planetary gear 5 is prevented from moving in the radial direction. As a result, the planetary gear 5 can be prevented from vibrating in the radial direction. Thus, vibrations of a planetary gear apparatus can be reduced, and the planetary gear and a carrier can be reduced in damage.

Abstract: A casing 23 of a second differential gear mechanism 2 is constituted by a carrier 19 and a sun gear 22 which are separately formed. Owing to this arrangement, the casing 23 is divided into two parts in a direction of its axis. The carrier 19 is movable in a direction of an axis L. By meshing engagement between a pinion gear 26 and a side gear 27A, the carrier 19, which forms a part of the casing 23, is press contacted with a housing 11 through a washer 29.

Abstract: Five receiving holes 2e extending along the axis of a circular cylindrical portion 2b of a housing are formed in the circular cylindrical portion 2b. Those five receiving holes 2e are arranged at equal intervals in the peripheral direction of the circular cylindrical portion 2b. Each receiving hole 2e rotatably receives therein a planetary gear 5. The respective planetary gears 5 are in engagement with an inner gear 3 and a sun gear 4. The teeth of the inner gear 3, the sun gear 4 and the planetary gears 5 are helical teeth. The numbers of teeth of the inner gear 3, the sun gear 4 and the planetary gears 5 are set to 36, 24 and 6, respectively. As a result, the numbers of teeth of the inner gear 3 and the sun gear 4 located between adjacent two planetary gears 5 in the peripheral direction become 7.2 and 4.8, respectively, which are values each having a fraction below the decimal point.

Abstract: A housing (10) has a planetary gear mechanism (20) composed of an inner gear (21), a planetary gear (22) and a sun gear (23), which mechanism is disposed within the housing (10) on its outer periphery side. The inner gear (21) is connected with a casing (31) arranged on a rotation axis (L). A spherical receiving portion (31a) is formed on the casing (31). This receiving portion (31a) is received in the sun gear (23). A pair of element gears (33, 33) and a pair of side gears (34, 34) of the planetary gear mechanism (30) are received in the receiving portion (31a).

Abstract: A carrier 2 is fixed to one end opening part of a circular cylindrical apparatus main body 1. A plurality of receiving holes 2d, which extend in parallel with a rotation axis L, are formed in the carrier 2 at the same interval in a peripheral direction. A planetary gear 4 is received in each receiving hole 2d such that the planetary gear 4 can rotate on its own axis. An inner gear 5 and a sun gear 9, which are arranged with their axes aligned with the rotation axis L of the apparatus main body 1, are disposed within the apparatus main body 1. The inner gear 5 is engaged with the planetary gears 4 at the outside thereof. The sun gear 9 is engaged with the planetary gears 4 at the inner side thereof. An engagement part between the inner gear 5 and the planetary gear 4 and an engagement part between the sun gear 9 and the planetary gear 4 are displaced from each other in a direction of the rotation axis L so that they are not overlapped with each other in a direction of the rotation axis L.

Abstract: A planetary gear 5 is contacted at its at least one tooth of all its teeth 51n with an end edge 23d facing an inner releasing part 23c of an inner peripheral surface of a receiving hole 23a irrespective of a rotational position of the planetary gear 5. By doing so, the planetary gear 5 is prevented from moving in the radial direction. As a result, the planetary gear 5 can be prevented from vibrating in the radial direction. Thus, vibrations of a planetary gear apparatus can be reduced, and the planetary gear and a carrier can be reduced in damage.

Abstract: A planetary gear mechanism 3 is provided at one end portion of a housing 2 in a direction of the rotation axis L. The planetary gear mechanism 3 comprises a planetary gear 31 which is disposed at the housing 2 such that the planetary gear 31 is rotatable about its own axis and revolvable about the rotation axis L in unison with the housing 2, and an inner gear 33 and a sun gear 34 which are in meshing engagement with the planetary gear 31 at its outer side and inner side, respectively. A differential gear mechanism 4 is provided at the other end portion of the housing 2 in a direction of the rotation axis L.

Abstract: A receiving portion 2e for rotatably receiving therein a planetary gear 3, is formed between a plurality of retaining protrusions 2d of a carrier. A connection portion 2f extending annularly about a rotation axis L is formed on an outer peripheral of a distal end portion of each retaining protrusion 2d. Through this connection portion 2f, the distal end portions of the respective retaining protrusions 2d are connected to each other. Owing to this arrangement, each retaining protrusion 2d is reinforced to minimize its deformation. As a result, deformation of the receiving portion 2e is greatly reduced and the planetary gear 3 receiving in the receiving portion 2e can rotate smoothly.

Abstract: A casing 23 of a second differential gear mechanism 2 is constituted by a carrier 19 and a sun gear 22 which are separately formed. Owing to this arrangement, the casing 23 is divided into two parts in a direction of its axis. The carrier 19 is movable in a direction of an axis L. By meshing engagement between a pinion gear 26 and a side gear 27A, the carrier 19, which forms a part of the casing 23, is press contacted with a housing 11 through a washer 29.

Abstract: In order to rotationally drive a gear material (3) when the gear material (3) is gear machined using a hob (not shown), a drive hole (34) having a circular configuration in section and extending on an axis L of the gear material (3) is formed in an end face (3e) of the gear material (3) and a shaft member (4) having a polygonal configuration is employed. The distance from an axis of this shaft body (4) to each angular portion (4a) is larger than the radius of the drive hole (34). The distance from the axis of the shaft member (4) to each side portion (4b) of the shaft member (4) is smaller than the radius of the drive hole (34). The shaft member (4) is fitted, under pressure, in the drive hole (34) and the gear member (3) is rotationally driven through this shaft member (4).

Abstract: A housing (2) includes first and second housing components (3A, 3B). The first and second components (3A, 3B) are fixed by bolts (6). Each bolt (6) extends through a central portion of a planet gear (72) of a planetary gear mechanism (7). The planet gear (72) is rotatably supported on the housing (3) through the bolts (6).

Abstract: Paired planetary gears 3A, 3B are each provided on one end thereof with a long gear portion 31, on the other end with a short gear portion 32, and a neck portion 33 between the long gear portion 31 and the short gear portion 32. The long gear portion 31 of the planetary gear 3A is in engagement with the short gear portion 32 of the other planetary gear 3B at an inner gear portion 31b and with a gear portion 2a of a side gear 2A at an outer gear portion 31a. The long gear portion 31 of the other planetary gear 3B is in engagement with the short gear portion 32 of the planetary gear 3A at the inner gear portion 31b and with a gear portion 2b of a side gear 2B at the outer gear portion 31a.