Honda Giken Kogyo Kabushiki Kaisha

Honda Motor Co., Ltd.

Takashi Hotta

Kimihiko Kikuchi

Yoichi Kojima

Tsunefumi Niiyama

Yorinori Kumagai

Yukio Morita

Hiroshi Nakayama

Takamichi Shimada

Tomoharu Kumagai

Shinichi Sakaguchi

Masao Nishikawa

Hiroshi Gomi

Masato Hirose

Tadanobu Takahashi

Masaru Ozawa

Kazuma Hatakeyama

Tomokazu Takeda

Motonori Ohnuki

Nobuo Takemasa

Fumihiro Yoshino

Moriaki Tokuda

Yoshihiro Yoshimura

Tetsu Kanou

Shuji Ueda

Tadami Kondoh

Kazuya Kubo

Tetsuya Ohtani

Kinji Marumo

Michio Kojima

Tadayasu Sanpe

Hisami Miyazaki

An input shaftis connected rotationally with an intermediary shaftthrough a connecting drive gear GCV, a connecting first idle gear GC, a connecting second idle gear GCand a connecting driven gear GCN. A fourth speed drive gear GV, which is formed in a one-piece body with a reverse drive gear GRV, is provided rotatably over the input shaft, and a third speed drive gear GV is provided rotatably over the intermediary shaft. Both the third speed drive gear GV and the fourth speed drive gear GV mesh with a third and fourth speed driven gear GN, which is provided rotatably over an output shaft. Also, a reverse driven gear GRN, which is connected rotationally with the reverse drive gear GRV through a reverse idle gear GRI, is provided rotatably over the output shaft

Parallel shaft transmission

In a transmission in which transmission mechanisms (1 speed, 2 speed, 3 speed and reverse transmission mechanisms ) are disposed between transmission input and output shafts which are parallel with each other, a structure in which a driving force is distributed from the output shaft for transmission to front and rear wheels of a vehicle comprising an intermediate rear wheel driving gear rotatably disposed on the input shaft , a front wheel side driving gear fixed to the output shaft for transmitting the driving force to the front wheels, a first rear wheel driving gear fixed to the output shaft so as to mesh with the intermediate gear and a second rear wheel driving gear rotatably disposed on a rear wheel driving rotating shaft which is parallel with the input shaft and adapted to mesh with the intermediate rear wheel driving gear so as to transmit the driving force to the rear wheels.

Driving force distributing structure for four wheel drive vehicle

A driven gear G for a forward second gear G which is obtained by a hydraulic clutch C on a second input shaft is disposed contiguous with a driven gear G for a first gear G . A spacer collar is provided on an output shaft so as to be positioned between a selector hub and the driven gear G for the second gear G , and the driven gear G for the first gear G is rotatably supported on the spacer collar

Three parallel shaft type automatic transmission

A ring gear support member is supported radially immovably on the outer circumference of an input shaft through a ball bearing. A brake hub of a reverse brake, as supported by the ring gear support member, is made movable in the circumferential direction relative to the ring gear support member and is urged to a center position by a coil spring. When the reverse brake is applied to couple the ring gear support member unrotatably to a casing, the brake hub is supported through the coil spring by the ring gear support member. As a result, the meshing vibration, as generated at the meshing portion between pinions and a ring gear, can be prevented from being transmitted to the casing through the brake hub, thereby reducing noise.

Planetary gear mechanism

An oil sump 44 and a second oil supply passage 45, which are to lead lubrication oil from a first oil supply passage 43 to where lubrication is needed, i.e., to gears and a clutch, are formed in a sun gear 21, which has a sufficient strength as a torque transmission member. In comparison with another case where an oil sump and an oil supply passage are provided in a relatively thin member such as a sleeve 3, the unfavorable effect of stress concentration around the oiling aperture and of deterioration of strength from the reduced thickness can be greatly minimized. In addition, the fabrication of the oil sump and the oil supply passage is much easier and cost-effective than if they were to be provided in a thinner member.

Lubrication structure for planetary gear assembly

A planetary gear transmission comprises first, second and third planetary gear trains G1, G2 and G3 which are disposed coaxially with one another and respectively in this order from an input member. The first and second ring gears R1 and R2, which are fixedly retainable by a first brake B1, are disengageably connected to the input shaft 1 through a first clutch K1. The first sun gear S1 is also disengageably connected to the input shaft 1 through a third clutch while the first carrier C1 and the second sun gear S2 are connected to the output shaft 7. Furthermore, a connecting shaft 4 is disposed away from and in parallel with the axis of the first, second and third planetary gear trains G1, G2 and G3, and one end of the connecting shaft is connected to the input shaft 1 through a first connecting gear train 2 and 3 while the other end of the connecting shaft is connected to the third sun gear S3 through a second connecting gear train 5 and 6.

Planetary gear transmission

A planetary gear device P includes a planetary carrier 3 integrally provided with a shaft portion 3.sub.1, a ring gear supporting member 7 having a ring gear 6 fixedly mounted on the outer periphery thereof, and an output member 10 spline-connected to the outer periphery of the shaft portion 3.sub.1. The right side of the ring gear supporting member 7 is supported on the left side of the planetary carrier 3 through a first thrust bearing 13, and the left side of the ring gear supporting member 7 is supported through a second thrust bearing 16 on the right side of a washer 15 secured to the shaft portion 3.sub.1, of the planetary carrier 3 by means of a circlip 14. With this arrangement, it is possible to reduce vibrations transmitted from the ring gear supporting member 7 of the planetary gear device P to the output member 10, to improve the mounting property of the planetary gear device P and to facilitate the management of dimensions of parts.

Supporting structure of a ring gear supporting member in planetary gear

A planetary gear transmission comprises a first planetary gear train of double pinion type G1 and second and third planetary gear trains of single pinion type G2 and G3 disposed coaxially and in parallel with one another. In this transmission, a first sun gear S1 is coupled to an input member 11 through a first clutch K1, and a first brake B1 is provided for the purpose of selectively holding the first sun gear S1 against rotation. First and second carriers C1 and C2 and a third ring gear R3 are coupled to one another, and these three elements are coupled to the input member 11 through a second clutch K2, and a second brake B2 is provided for the purpose of selectively holding these three elements against rotation. A first ring gear R1 and a second ring gear R2 are coupled with each other, and a third brake B3 is provided for the purpose of selectively holding these two elements against rotation. Second and third sun gears S2 and S3 are coupled with each other, and these two elements are coupled to the input member 11 through a third clutch K3. A third carrier C3 is directly coupled to an output member 12.

A planetary gear mechanism includes a planetary carrier and pinions rotatably carried on the planetary carrier through pinion shafts. An annular lubricating oil supply member is mounted on a ring gear supporting member which supports a ring gear on its outer periphery and which is rotatable. The lubricating oil supply member has a plurality of fins formed radially thereon. The lubricating oil received within the lubricating oil supply member while submerged in the lubricating oil is scattered by a centrifugal force and supplied to oil reservoirs defined in the adjacent side of the planetary carrier and then from the oil reservoirs via oil passages in the pinion shafts to the needle bearing which supports the pinions. With the above construction, it is possible to effectively supply the lubricating oil to the pinion shafts of the planetary gear mechanism when the planetary is in a fixed position.

Lubricating oil supply structure in planetary gear mechanism

A planetary gear transmission typically for use on automobiles has first, second, and third planetary gear trains arranged coaxially with each other and each having elements including a sun gear, a carrier, and a ring gear. Two of the elements of each of the first, second, and third planetary gear trains are directly or disengageably coupled to elements of the other planetary gear trains. The transmission also has three clutch means and two brake means for selectively establishing a power transmitting path from an input shaft to an output gear member through the first, second, and third planetary gear trains. At least one of the first, second, and third planetary gear trains comprises a double-pinion planetary gear train, one of the sun gear and the carrier of the double-pinion planetary gear train being coupled to the input shaft and the other being nonrotatably fixed. The elements of the first, second, and third planetary gear trains are corotatably coupled into first, second, third, fourth, and fifth rotational members in a speed diagram, the third and fifth rotatable members being coupled to the input member, the fourth rotational member being coupled to the output member and. The carrier of the double-pinion planetary gear train may be coupled to the input shaft, and the sun gear thereof may be nonrotatably fixed.

A planetary gear transmission typically for use on automobiles has first, second, and third planetary gear trains arranged coaxially with each other and each having elements including a sun gear, a carrier, and a ring gear. Two of the elements of each of the first, second, and third planetary gear trains are directly or disengageably coupled to elements of the other planetary gear trains between input and output members. The elements of the first, second, and third planetary gear trains are corotatably coupled into first, second, third, fourth, and fifth rotational members the first, second, and fifth rotational members being coupled to the input member, the fourth rotational member being coupled to the output member. The planetary gear transmission also has a separating clutch disposed between the elements of the second rotational member, for disengageably connecting the elements of the second rotational member.

Clutch-separable planetary gear transmission

An armature winding structure for use in an electric motor includes a web-shaped strand bundle composed of a plurality of parallel strands. The strand bundle has a plurality of longitudinally spaced bends and a plurality of straight strand bundle segments. Adjacent ones of the strand bundle segments are positioned one on each side of one of the bends. The strand bundle segments are transversely staggered on one side of the strand bundle successively from one end to the other of the strand bundle, by intervals each substantially equal to the width of the strand bundle. The strand bundle segments thus staggered are longitudinally folded over along fold lines extending respectively across or near the bends transversely of the strand bundle, thereby providing a plate-like winding in which the strand bundle segments lie adjacent to one another.

Armature winding structure for electric motors

A planetary gear transmission typically for use on automobiles has first, second, and third planetary gear trains arranged coaxially with each other and each having elements including a sun gear, a carrier, and a ring gear. Two of the elements of each of the first, second, and third planetary gear trains are directly or disengageably coupled to elements of the other planetary gear trains. The transmission also has two clutch means and three brake means for selectively establishing a power transmitting path from an input shaft to an output gear member through the first, second, and third planetary gear trains. The first planetary gear train comprises a double-pinion planetary gear train, one of the sun gear and the carrier of the double-pinion planetary gear train being coupled to the input shaft and the other being disengageably coupled to a stationary member. The elements of the first, second, and third planetary gear trains are corotatably coupled into first, second, third fourth, and fifth rotational members in a speed diagram, the third and fifth rotatable members being coupled to the input member, the fourth rotational member being coupled to the output member.

A planetary gear transmission for use on automobiles includes an input shaft, an output gear, and three planetary gear trains disposed coaxially with each other and each having a sun gear element, a carrier element, and a ring gear element, two of the elements of each of the planetary gear trains being mechanically coupled to elements of the other planetary gear trains for rotation therewith. The elements which are mechanically coupled to each other provide first through fifth rotating members, the first and fifth rotating members being coupled to the input shaft, one of the second and third rotating members being coupled to the output gear, the fourth rotating member being coupled to the output gear. The planetary gear transmission also has a separating clutch disposed between the elements of the third rotating member, for selectively engaging and disengaging the elements of the third rotating member.

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Saitama, Japan

Takashi Hotta