JP7091884B2 - Automatic transmission - Google Patents

Description

The present invention relates to an automatic transmission.

Conventionally, in automatic transmissions mounted on vehicles such as automobiles, the oil gutter catches the oil that is scraped up and scattered by the rotation of the gears and guides it to the parts that require lubrication to improve the lubrication performance. An automatic transmission is known (see Patent Document 1). In addition, a transmission that improves lubrication performance by guiding oil to a part requiring lubrication using an oil pump is also known.

Japanese Unexamined Patent Publication No. 60-215159

However, in the case described in Patent Document 1, the oil gutter 10 is used to remove the lubricating oil that is scraped up by the transmission gear 3 arranged on the drive shaft 2 arranged above in the casing 1 and adheres to the inner wall 1a of the casing 1 and flows down. It was accepted, and there was a problem with the collection performance of the oil gutter 10. Further, regarding the transmission provided with the oil pump, there is a problem that the cost of the transmission is increased by providing the oil pump.

The present invention has been made by paying attention to the above circumstances, and an object of the present invention is to provide an automatic transmission capable of improving lubrication performance without providing an oil pump.

The present invention includes a transmission including an input shaft arranged parallel to each other , a counter shaft arranged below the input shaft, and an output shaft arranged coaxially with the input shaft in order to achieve the above object. And a transmission case having a transmission chamber for accommodating the transmission, and an oil gutter provided at the upper part of the transmission chamber to receive the oil scraped up by the gear of the transmission and guide it to a part requiring lubrication. The automatic transmission is provided with a reverse idler shaft provided with a reverse idler gear directly under the oil gutter, and the counter shaft is used for a forward stage that meshes with the reverse idler gear. A plurality of speed change gears including the 1st speed counter gear are provided, and the 1st speed counter gear is the largest diameter gear among the plurality of the speed change gears on the counter shaft, and is rearward of the other speed change gears. It is characterized by being arranged .

As described above, according to the present invention, the lubrication performance can be improved without providing an oil pump.

FIG. 1 is a side view of an automatic transmission according to an embodiment of the present invention as viewed from the left side of the vehicle. FIG. 2 is a plan view of an automatic transmission according to an embodiment of the present invention. FIG. 3 is a cross-sectional view taken along the line III-III in FIG. FIG. 4 is an enlarged cross-sectional view of the torque converter housing and the front case of FIG. FIG. 5 is a cross-sectional view taken along the line VV of FIG. FIG. 6 is a cross-sectional view taken along the line in the VI-VI direction of FIG.

An automatic transmission according to an embodiment of the present invention houses a transmission including an input shaft and a counter shaft arranged parallel to each other and an output shaft arranged coaxially with the input shaft, and a transmission. An automatic transmission equipped with a transmission case having a transmission chamber and an oil gutter at the upper part of the transmission chamber that receives the oil scraped up by the gears of the transmission and guides it to a part requiring lubrication. The machine is characterized by having a reverse idler shaft provided with a reverse idler gear directly under the oil gutter. Thereby, the automatic transmission according to the embodiment of the present invention can improve the lubrication performance without providing an oil pump.

Hereinafter, the automatic transmission according to an embodiment of the present invention will be described with reference to the drawings. 1 to 6 are views showing an automatic transmission according to an embodiment of the present invention. In FIGS. 1 to 6, in the up / down / front / rear / left / right directions, the width direction of the vehicle is the left / right direction and the height direction of the vehicle is the up / down direction when the traveling direction of the vehicle is the front and the backward direction is the rear. Further, the width direction of the vehicle is also referred to as the vehicle width direction.

First, the configuration will be described. In FIGS. 1 and 2, an automatic transmission 2 is mounted on the vehicle 1, and the automatic transmission 2 is fixed to an engine 3 as a driving force source and an internal combustion engine, and is attached to a floor panel 1A of the vehicle 1. It is installed vertically below. That is, the vehicle 1 of this embodiment is a rear-wheel drive vehicle.

The automatic transmission 2 includes a transmission case 4, and the transmission case 4 includes a torque converter housing (hereinafter, simply referred to as a torque converter housing) 5, a front case 6, a rear case 7, and an extension case 8. There is. The front end of the transmission case 4 is connected to the engine 3 by a bolt (not shown). Of the transmission cases 4, the front case 6, the rear case 7, and the extension case 8 excluding the torque converter housing 5 constitute the transmission case main body 40. That is, the transmission case 4 includes a torque converter housing 5 and a transmission case main body 40.

The automatic transmission 2 includes a shift unit 100, and the shift unit 100 drives the automatic transmission 2 to perform a shift operation and a clutch operation. Here, the shift operation means an operation of switching the shift stage of the automatic transmission 2, and the clutch operation means engaging (connecting) or releasing (disconnecting) the friction clutch 17 (see FIG. 3) of the automatic transmission 2. The operation to be performed.

In FIGS. 3 and 4, the torque converter 10 is housed in the torque converter housing 5. The torque converter 10 includes a front cover 10A connected to a crank shaft (not shown) of the engine 3 and a shell 10B connected to the front cover 10A, and powers the automatic transmission 2 from the engine 3 via oil. Is communicating.

A pump impeller (not shown) is fixed to the inner surface of the shell 10B. Inside the shell 10B, a turbine runner (not shown) is installed facing the pump impeller, and the turbine runner is connected to the turbine shaft 11. A stator (not shown) is installed between the pump impeller and the turbine runner.

When the crank shaft of the engine 3 rotates, the front cover 10A, the shell 10B, and the pump impeller rotate integrally in the torque converter 10. At this time, due to the centrifugal force due to the rotation of the pump impeller, a flow from the pump impeller to the turbine runner is generated in the fluid inside the torque converter 10. The stator converts the flow of fluid from the turbine runner along the direction of rotation of the pump impeller. The torque converter 10 amplifies the power received from the engine 3 by the torque amplification action and outputs it from the turbine shaft 11.

A ring gear 10C is provided on the outer peripheral portion of the shell 10B. The ring gear 10C transmits the rotation of the starter to the engine 3 by engaging the pinions of the starter (not shown) when the engine 3 is started.

The torque converter housing 5 has a peripheral wall 51 that surrounds the torque converter 10 from the outer peripheral side, and a partition wall 55 that is provided inside the peripheral wall 51 and supports the turbine shaft 11 between the torque converter 10 and the friction clutch 17. ..

The partition wall 55 separates the torque converter chamber 81 inside the torque converter housing 5 and the clutch chamber 82 inside the front case 6. The turbine shaft 11 is rotatably supported via a bearing 38A in a bearing portion formed on the partition wall 55.

An oil pump 12 is housed in the torque converter housing 5, and the oil pump 12 is composed of, for example, a trochoid type oil pump. The oil pump 12 includes a pump housing 12A, which is a second pump housing 14 fixed to a partition wall 55 by a bolt (not shown) and a first pump fastened to the second pump housing 14 by a bolt (not shown). It consists of a housing 13. The first pump housing 13 and the second pump housing 14 constitute a housing of the oil pump 12. A pump chamber 15 is formed inside the first pump housing 13 and the second pump housing 14, and an inner rotor and an outer rotor (not shown) are provided in the pump chamber 15. The inner rotor is attached to the shell 10B via the impeller hub and rotates integrally with the shell 10B.

The outer rotor is provided on the outer side in the radial direction of the inner rotor, and rotates with the rotation of the inner rotor. The trochoid type oil pump 12 forms an operating chamber (not shown) for accommodating oil between the external teeth and the internal teeth by contacting the internal teeth formed on the outer rotor and the external teeth formed on the inner rotor. ..

When the power of the engine 3 is transmitted to the inner rotor via the front cover 10A, the inner rotor and the outer rotor rotate in one direction in the oil pump 12. At this time, the volume of the working chamber increases and decreases continuously, so that the oil is sucked into the working chamber and the oil is discharged from the working chamber.

A disk-shaped flange portion 11A is formed at the rear end portion of the turbine shaft 11, and the flange portion 11A is formed to have a larger diameter than the front end portion and the central portion of the turbine shaft 11. An annular flywheel 16 is attached to the flange portion 11A. The flywheel 16 is a friction engaging element of the friction clutch 17. Therefore, the friction clutch 17 is connected to the turbine shaft 11. The flywheel 16 is housed in the front case 6.

A friction clutch 17 and a transmission 20 are housed in the front case 6, and the friction clutch 17 faces the flywheel 16 in the axial direction.

The front case 6 includes a peripheral wall 61 that surrounds the friction clutch 17 and the transmission 20 from the outer peripheral side, a clutch chamber 82 in which the friction clutch 17 is housed, and a transmission room 83 in which the transmission 20 is housed inside the peripheral wall 61. It has a partition wall 65 and a partition wall 65.

The rear case 7 has a peripheral wall 71 that surrounds the transmission 20 from the outer peripheral side, and a partition wall 75 that supports the rotation axis of the transmission 20. The partition wall 75 is formed at the rear end portion of the rear case 7, and an opening through which the output shaft 22 and the counter shaft 23 pass is formed. The extension case 8 is attached to the rear end of the rear case 7, has an opening for extracting driving force from the output shaft 22, and seals the internal space of the transmission chamber 83.

The friction clutch 17 is attached in the vicinity of the front end portion 21a in the axial direction of the input shaft 21. The input shaft 21 is housed in the front case 6 and the rear case 7, is rotatably supported by the flange portion 11A via the bearing 38B at the front end portion 21a in the axial direction, and is rotatably supported by the flange portion 11A at the rear end portion 21b in the axial direction. It is rotatably supported.

The output shaft 22 is arranged coaxially with the input shaft 21 behind the input shaft 21 in the axial direction of the input shaft 21. The output shaft 22 is rotatably supported by the partition wall 75 at the rear end of the rear case 7 and the extension case 8 via bearings 38D and 38E, respectively. The output shaft 22 rotates relative to the input shaft 21.

The friction clutch 17 includes a clutch disc 17A provided so as to be integrally rotatable with the input shaft 21 and movable in the axial direction of the input shaft 21, a pressure plate 17B for pressing the clutch disc 17A against the flywheel 16, and a pressure plate 17B. It is equipped with a diaphragm spring 17C that urges the flywheel 16 side.

The partition wall 65 of the front case 6 is formed with a tubular portion 66 through which the input shaft 21 passes, and the tubular portion 66 is on the friction clutch 17 side from the vicinity of the center of the partition wall 65 along the axial direction of the input shaft 21. Extends to. That is, the tubular portion 66 is formed so as to project from the partition wall 65 toward the clutch chamber 82. The input shaft 21 is supported on the inner circumference of the tubular portion 66 via a bearing 38C.

A release bearing 18 is provided on the outer peripheral portion of the tubular portion 66 so as to be adjacent to the friction clutch 17 in the axial direction. The release bearing 18 moves in the axial direction of the input shaft 21 to come into contact with and separate from the diaphragm spring 17C in the radial direction.

When the release bearing 18 is moved forward in the axial direction of the input shaft 21 by the release lever 19, it presses the radial inner end portion of the diaphragm spring 17C forward. As a result, the urging of the pressure plate 17B is released, and the clutch disc 17A is not pressed against the flywheel 16. As a result, the friction clutch 17 is released, and the rotation of the crank shaft of the engine 3 is not transmitted to the input shaft 21.

When the release bearing 18 is moved rearward with respect to the axial direction of the input shaft 21 by the release lever 19, it separates from the radial inner end portion of the diaphragm spring 17C. At this time, the diaphragm spring 17C urges the pressure plate 17B to press the clutch disc 17A against the flywheel 16, so that the rotation of the flywheel 16 (rotation of the crank shaft of the engine 3 via the torque converter 10) is input. Communicate to 21. In this way, the friction clutch 17 switches the power transmission state between the crank shaft of the engine 3 and the input shaft 21 to the transmission state or the cutoff state.

The counter shaft 23 is housed in the front case 6 and the rear case 7, and the counter shaft 23 is rotatably supported by the partition wall 65 of the front case 6 and the extension case 8. The counter shaft 23 extends parallel to the input shaft 21 and the output shaft 22.

The input shaft 21 is provided with a 4-speed input gear 24A, a 3-speed input gear 24B, a 2-speed input gear 24C, a 1-speed input gear 24D, and a reverse input gear 24E from the friction clutch 17 side toward the output shaft 22. ..

The 4th speed input gear 24A, the 3rd speed input gear 24B, the 2nd speed input gear 24C, the 1st speed input gear 24D, and the reverse input gear 24E are rotatably connected to the input shaft 21.

A 5-speed clutch gear 22A is provided at the front end of the output shaft 22, and the 5-speed clutch gear 22A is composed of a dog formed on the outer peripheral portion of the output shaft 22.

The counter shaft 23 is provided with a 4-speed counter gear 26A, a 3-speed counter gear 26B, a 2-speed counter gear 26C, a 1-speed counter gear 26D, and a counter drive gear 26E from the friction clutch 17 side toward the output shaft 22. ..

The 4-speed counter gear 26A, the 3-speed counter gear 26B, the 2-speed counter gear 26C, the 1-speed counter gear 26D, and the counter drive gear 26E are fixed to the counter shaft 23.

The 4th speed counter gear 26A, the 3rd speed counter gear 26B, the 2nd speed counter gear 26C, and the 1st speed counter gear 26D are the 4th speed input gear 24A, the 3rd speed input gear 24B, and the 2nd speed input gear 24C, which form the same gear. It meshes with the 1st speed input gear 24D.

The counter drive gear 26E meshes with the counter driven gear 27, and the counter driven gear 27 is fixed to the output shaft 22 so as to rotate integrally with the output shaft 22.

The front case 6 and the rear case 7 include a synchronization device 28 for 3rd and 4th speeds, a synchronization device 29 for 1st and 2nd speeds, and a synchronization device 30 for reverse and 5th speeds.

The synchronization device 28 for 3rd and 4th speeds is rotatable integrally with the input shaft 21 and is movably provided in the axial direction of the input shaft 21. When the shift and select shaft 33 is operated, the synchronization device 28 for the 3rd and 4th speeds has the input shaft 21 via the shift shaft, the shift yoke and the shift fork for the 3rd and 4th speeds (not shown). Moved in the axial direction.

The 1st / 2nd speed synchronization device 29 is rotatable integrally with the input shaft 21 and is movably provided in the axial direction of the input shaft 21. When the shift and select shaft 33 is operated, the 1st / 2nd speed synchronization device 29 of the input shaft 21 via the 1st / 2nd speed shift shaft, shift yoke and shift fork (not shown). Moved in the axial direction.

The reverse-5-speed synchronization device 30 is rotatable integrally with the input shaft 21 and is movably provided in the axial direction of the input shaft 21. When the shift-and-select shaft 33 is operated, the reverse-5-speed synchronous device 30 has an axial direction of the input shaft 21 via a reverse-5-speed shift shaft, a shift yoke, and a shift fork (not shown). Will be moved to.

The synchronization device 28 for 3rd and 4th speeds moves from the neutral position to the front side in the axial direction of the input shaft 21 to connect the 4th speed input gear 24A to the input shaft 21 to establish a forward 4th speed stage. The power of the input shaft 21 is transmitted to the counter shaft 23 via the 4-speed input gear 24A and the 4-speed counter gear 26A.

The power transmitted to the counter shaft 23 is transmitted from the counter drive gear 26E to the output shaft 22 via the counter driven gear 27. A differential device (not shown), a drive shaft, and a drive rear wheel are connected to the output shaft 22 via a propeller shaft (not shown).

As a result, the power transmitted to the output shaft 22 is transmitted to the differential device via the propeller shaft, then distributed to the left and right drive shafts by the differential device, and is transmitted from the drive shaft to the drive rear wheels. As a result, the vehicle 1 is driven.

The synchronization device 28 for 3rd and 4th speeds connects the 3rd speed input gear 24B to the input shaft 21 by moving from the neutral position to the rear side in the axial direction of the input shaft 21 to establish a forward 3rd speed stage. , The power of the input shaft 21 is transmitted to the counter shaft 23 via the 3rd speed input gear 24B and the 3rd speed counter gear 26B.

The 1st / 2nd speed synchronization device 29 moves from the neutral position to the front side in the axial direction of the input shaft 21 to connect the 2nd speed input gear 24C to the input shaft 21 to establish a forward 2nd speed stage. The power of the input shaft 21 is transmitted to the counter shaft 23 via the second speed input gear 24C and the second speed counter gear 26C.

The 1st / 2nd speed synchronization device 29 moves from the neutral position to the rear side in the axial direction of the input shaft 21 to connect the 1st speed input gear 24D to the input shaft 21 to establish a forward 1st speed stage. , The power of the input shaft 21 is transmitted to the counter shaft 23 via the 1st speed input gear 24D and the 1st speed counter gear 26D.

The reverse-5-speed synchronous device 30 moves from the neutral position to the front side in the axial direction of the input shaft 21 to connect the reverse input gear 24E to the input shaft 21 to establish a reverse stage, and the reverse stage 21 is established. Power is transmitted from the reverse input gear 24E to the counter shaft 23 via the reverse idler gear 25A (see FIG. 5, first idler gear 25B, second idler gear 25C) and the first speed counter gear 26D, which will be described later. At this time, since the counter shaft 23 rotates in the direction opposite to the rotation direction at the time of forward movement, the vehicle 1 is moved backward.

The reverse-5th speed synchronization device 30 moves from the neutral position to the rear side in the axial direction of the input shaft 21 to connect the 5th speed clutch gear 22A to the input shaft 21 to establish a forward 5th speed stage. The power of the input shaft 21 is directly transmitted to the output shaft 22.

A shift case 9 is provided on the upper portion of the front case 6, and a shift and select shaft 33 is provided inside the shift case 9. The shift and select shaft 33 extends in the vehicle width direction orthogonal to the extending direction of the input shaft 21.

The shift-and-select shaft 33 is provided in the shift case 9 so as to be rotatable and axially movable, and is operated by a shift unit 100 connected to an end thereof.

An oil pan 41 is attached to the lower part of the front case 6, and an oil storage chamber 43 for storing oil is formed inside the oil pan 41. The oil storage chamber 43 is arranged below the clutch chamber 82. Further, a valve body 42 is housed between the oil pan 41 and the lower portion of the front case 6, and the valve body 42 is fastened to the lower portion of the front case 6 by bolts (not shown).

The valve body 42 supplies the oil sucked up from the oil pan 41 by the oil pump 12 to the torque converter 10 through the inside of the torque converter housing 5.

The oil supplied to the torque converter 10 is used as oil for engaging or disengaging a lockup clutch (not shown) of the torque converter 10, or oil flowing from the pump impeller to the turbine runner.

Further, the valve body 42 supplies the oil sucked up from the oil pan 41 by the oil pump 12 to a portion requiring lubrication such as the bearing 38A through the inside of the torque converter housing 5.

The release lever 19 is arranged on the side opposite to the friction clutch 17 with respect to the release bearing 18 in the axial direction of the automatic transmission 2. That is, the friction clutch 17 is arranged in front of the release bearing 18, while the release lever 19 is arranged behind the release bearing 18.

The release lever 19 is connected to the shift unit 100 described above and is operated by the shift unit 100. Specifically, the release lever 19 is swingably supported by using a fulcrum member attached to the partition wall 65 of the front case 6 as a swinging fulcrum, and the end portion on the side connected to the shift unit 100 is one in the axial direction. When moved to, the end portion on the release bearing 18 side moves to the other side in the axial direction. The release lever 19 constitutes the release member in the present invention.

Specifically, the release lever 19 is swingably supported by the partition wall 65 of the front case 6 at the swing center thereof. One swing end 19A of the release lever 19 is connected to the release bearing 18, and the other swing end 19B of the release lever 19 is connected to the shift unit 100.

In this embodiment, the operating force of the shift unit 100 is transmitted to the release bearing 18 by the swinging motion of the release lever 19, but the release member for transmitting the operating force of the shift unit 100 to the release bearing 18 is It is not limited to the release lever 19. For example, as the release member, a member that transmits the operating force of the shift unit 100 to the release bearing 18 without swinging motion can also be used.

In FIG. 4, the front case 6 has a valve body chamber 84 that continuously stores the valve body 42 in the oil storage chamber 43 above the oil storage chamber 43, and separates the clutch chamber 82 and the valve body chamber 84. It has a ceiling wall 68 to be used. The rear end of the ceiling wall 68 is connected to the lower part of the partition wall 65, the right end of the ceiling wall 68 is connected to the lower right side of the peripheral wall 61, and the left end of the ceiling wall 68 is connected to the lower end of the vertical wall 69 described later. Further, the front end of the ceiling wall 68 is connected to the lower part of the peripheral wall 61.

As shown in FIGS. 4, 5, and 6, in this embodiment, the automatic transmission 2 has an input shaft 21 and a counter shaft 23 arranged parallel to each other, and an output shaft arranged coaxially with the input shaft 21. A transmission 20 including the 22 and a transmission case 4 having a transmission chamber 83 for accommodating the transmission 20 are provided.

Further, an oil gutter 90 is provided in the upper part of the transmission chamber 83 to receive the oil scraped up by the gear of the transmission 20 and guide it to a portion requiring lubrication.

In this embodiment, the transmission 20 has a reverse idler shaft 25 provided with a reverse idler gear 25A directly under the oil gutter 90. The counter shaft 23 mutually transmits power to and from the output shaft 22 so as to always rotate when the vehicle is running, and the reverse idler shaft 25 is such that the counter shaft 23 always rotates when the vehicle is running. Power is transmitted to each other. That is, in this embodiment, the output shaft 22 is configured to always rotate when the vehicle is running, and the reverse idler shaft 25 is configured to always rotate when the output shaft 22 rotates via the counter shaft 23. It meshes with the output shaft 22.

As shown in FIG. 5, the reverse idler shaft 25 is rotatably supported by a partition wall 65 of the front case 6 at its front end and a partition wall 75 of the rear case 7 at its rear end via bearings. Specifically, the front end of the reverse idler shaft 25 is a bearing holder formed on the rear surface (vertical wall facing rearward) of the bulging portion 65A that bulges rearward from the partition wall 65 of the front case 6 via the bearing 25D. The portion is pivotally supported via a bearing 25D. The rear end of the reverse idler shaft 25 is pivotally supported by a bearing holding portion formed on the partition wall 75 of the rear case 7 via the bearing 25E. The bulging portion 65A bulges rearward from the partition wall 65 to the vicinity of the mating surface of the front case 6 and the rear case 7 in the axial direction. Further, the reverse idler gear 25A includes a first idler gear 25B that meshes with a gear (1st speed counter gear 26D) arranged on the counter shaft 23 and a second idler gear that meshes with a gear (reverse input gear 24E) arranged on the input shaft 21. It is composed of 25C.

That is, the reverse idler gear 25A is a general term for the first idler gear 25B and the second idler gear 25C. The first idler gear 25B and the second idler gear 25C are fixed to the reverse idler shaft 25 so as to be adjacent to each other in the axial direction. Further, since the second idler gear 25C is formed to have a larger diameter than the first idler gear 25B, the outer peripheral edge of the second idler gear 25C is arranged so as to overlap the outer peripheral edge of the first speed counter gear 26D when viewed from the axial direction. ing. That is, the outer peripheral edge of the second idler gear 25C is located behind the meshing portion between the first speed counter gear 26D and the first idler gear 25B. Since FIG. 5 is a vertical cross section passing through the axis of the reverse idler gear 25A, the gears 26B, 26C, and 26D of the counter shaft 23 are only a part thereof in FIG.

The transmission case 4 has peripheral walls 61 and 71 that surround the transmission 20 from the outer peripheral side. On the side of the peripheral walls 61 and 71, the oil gutter 90 is arranged in the vicinity of the peripheral walls 61 and 71. As shown in FIG. 5, the oil gutter 90 is formed long in the front-rear direction along the reverse idler shaft 25. Regarding the bottom surface of the oil gutter 90, the bottom surface above the reverse idler gear 25A is higher than the bottom surface at the front position. That is, the bottom surface of the reverse idler gear 25A at the upper position where interference is a problem is set to a height closer to receive the oil scattered by the reverse idler gear 25A while ensuring a gap with the reverse idler gear 25A. ing. The bottom surface of the front part where the reverse idler gear 25A does not exist is set at a position lower than the upper position of the reverse idler gear 25A to expand the internal space of the oil gutter 90 to increase the oil capacity and the front of the oil. Is generating a flow to.

Further, as shown in FIG. 6, the oil gutter 90 has an oil receiving portion 91 for receiving oil on the side (left side) opposite to the peripheral wall 61. The oil receiving portion 91 extends to the left from the upper end of the wall on the left side of the oil gutter 90 and extends above the input shaft 21. Specifically, the oil receiving portion 91 is arranged above the shift shaft arranged above the input shaft 21, and is formed so as to extend diagonally upward to the left from the oil gutter 90. Then, the oil receiving unit 91 receives the oil scattered in the transmission chamber 83 and guides it to the oil gutter 90, and collects the oil that has been scraped up by the reverse idler gear 25A and has jumped over the oil gutter 90.

The oil gutter 90 drops oil on the upper surface 65B of the bulging portion 65A in order to supply oil to the bearing 25D on the front side of the reverse idler shaft 25. As shown in FIG. 5, since the upper surface 65B is formed downward, the oil dripping on the upper surface 65B flows toward the bearing 25D and flows into the oil introduction portion 65C formed in the bearing holding portion of the bearing 25D. Will reach the bearing 25D. A groove for guiding the flow of oil is formed on the upper surface 65B of the bulging portion 65A so as to guide the oil to the oil introducing portion 65C. The oil gutter 90 also has a function of an oil catch tank, and is adapted to store excess oil in the transmission chamber 83. The stirring resistance of the transmission can be reduced, and the fuel efficiency of the vehicle can be improved.

As shown in FIG. 6, the counter shaft 23 is arranged slightly to the right below the input shaft 21 and the output shaft 22 when viewed from the rear of the vehicle. Further, the reverse idler shaft 25 is located at a position substantially equal to the input shaft 21 and the output shaft 22 and is arranged on the right side in the transmission chamber 83. The oil gutter 90 is arranged on the upper right side of the transmission chamber 83 near the peripheral walls 61 and 71, and slightly on the left side above the reverse idler shaft 25.

As shown in FIG. 6, the rotation direction of each axis in the present embodiment when advancing is counterclockwise (counterclockwise) for the input axis 21, clockwise (clockwise) for the counter axis 23, and reverse idler axis. 25 is counterclockwise (counterclockwise).

The power transmission path of the reverse stage is the input shaft 21, the synchronization device 30, the reverse input gear 24E, the second idler gear 25C, the first idler gear 25B, the first speed counter gear 26D, the counter drive gear 26E, the counter driven gear 27, and the output shaft 22. be.

The 1st speed counter gear 26D of the counter shaft 23 is the gear having the largest diameter among the transmission gears on the counter shaft 23, and is arranged behind the other transmission gears. Therefore, the oil accumulated in the bottom of the transmission chamber 83 can be easily scraped up, and a large amount of oil can be supplied around the reverse idler shaft 25. Explaining with reference to FIG. 6, in the present embodiment, the first speed counter gear 26D rotates clockwise (clockwise) with a large amount of oil when moving forward. The 1st-speed counter gear 26D meshes with the 1st-speed input gear 24D before the 1st idler gear 25B, and the oil on the tooth surface flows out in the axial direction (front-rear direction) due to the meshing with the 1st-speed input gear 24D. However, since the 1st speed input gear 24D has a small diameter, the synchronization device 29 and the reverse input gear 24E exist before and after the meshing portion, and the oil flowing out in the axial direction (front-rear direction) is the synchronization device 29 and the reverse input gear 24E. The reverse idler gear 25A can be reached by being guided by.

Since the second idler gear 25C is formed to have a larger diameter than the first idler gear 25B and is arranged at a position closer to the rear than the first idler gear 25B, the oil supplied by the first speed counter gear 26D can be used more. You can receive a lot. Further, the outer periphery of the second idler gear 25C is close to the peripheral wall 61 of the transmission case 4, and as shown in FIG. 5, the peripheral wall 61 is downward toward the outer periphery of the second idler gear 25C. Since it is formed on the slope, more oil supplied by the 1st speed counter gear 26D can be scraped up. In FIG. 6, the reverse idler shaft 25 is counterclockwise (counterclockwise) when the vehicle is moving forward, and the reverse idler gear 25A can form an oil flow that flows upward along the peripheral wall 71. This oil flow is guided by the wall on the right side of the oil gutter 90 and the peripheral wall 71, passes between the wall on the right side of the oil gutter 90 and the peripheral wall 71, and reaches above the oil gutter 90. Since the inner surface of the transmission case 4 located above the oil gutter 90 is formed substantially horizontally by bending from the peripheral wall 71 that guides the oil, the flow of oil is stagnant at this portion and the accumulated oil is downward. It falls on the oil gutter 90 and the oil receiving portion 91 of the above, and is supplied to the inside of the oil gutter 90.

Next, the effect of the automatic transmission 2 configured as described above will be described.

In this embodiment, the transmission 20 includes an input shaft 21 and a counter shaft 23 arranged parallel to each other, and an output shaft 22 arranged coaxially with the input shaft 21. The transmission case 4 has a transmission chamber 83 for accommodating the transmission 20. An oil gutter 90 is provided in the upper part of the transmission chamber 83 to receive the oil scraped up by the gear of the transmission 20 and guide it to a portion requiring lubrication.

The transmission 20 has a reverse idler shaft 25 provided with a reverse idler gear 25A directly below the oil gutter 90.

As a result, since the reverse idler gear 25A is arranged directly under the oil gutter 90, the oil scattered by the rotation of the reverse idler gear 25A can be received by the oil gutter 90, and the received oil can be received by the bearing of the reverse idler shaft 25 or the reverse idler again. Since it can be supplied to the gear 25A, the lubrication performance of the reverse idler gear 25A can be improved. As a result, the lubrication performance can be improved without providing an oil pump.

Further, in this embodiment, the counter shaft 23 transmits power to and from the output shaft 22 so as to always rotate when the vehicle is running, and the reverse idler shaft 25 always rotates when the vehicle 1 is running. Power is transmitted to each other with the counter shaft 23 so as to do so.

As a result, the opportunity for the reverse idler gear 25A of the reverse idler shaft 25 to rotate increases, more oil can be supplied to the oil gutter 90, and the lubrication performance can be improved. In particular, it is important to improve the lubrication performance of the reverse idler shaft 25 that rotates not only during reverse travel but also during forward travel.

The reverse idler gear 25A is composed of a first idler gear 25B that meshes with a gear arranged on the counter shaft 23 and a second idler gear 25C that meshes with a gear arranged on the input shaft 21. The first idler gear 25B and the second idler gear 25C are fixed to the reverse idler shaft 25 adjacent to each other in the axial direction.

As a result, the adjacent first idler gear 25B and the second idler gear 25C rotate, so that more oil can be scraped up and supplied to the oil gutter 90, and the lubrication performance can be improved.

The transmission case 4 has peripheral walls 61 and 71 surrounding the transmission 20 from the outer peripheral side, and the oil gutter 90 is arranged in the vicinity of the peripheral walls 61 and 71. The oil gutter 90 has an oil receiving portion 91 that receives oil on the side opposite to the peripheral walls 61 and 71.

As a result, the oil gutter 90 can receive and take in the oil that has passed above the oil gutter 90 from the peripheral wall 61 side by the oil receiving portion 91. Therefore, more oil can be supplied to the oil gutter 90, and the lubrication performance can be improved.

Although embodiments of the present invention have been disclosed, it will be apparent to those skilled in the art that modifications may be made without departing from the scope of the invention. All such modifications and equivalents are intended to be included in the following claims.

2 ... Automatic transmission, 4 ... Transmission case, 20 ... Transmission, 21 ... Input shaft, 22 ... Output shaft, 23 ... Counter shaft, 25 ... Reverse idler Shaft, 25A ... Reverse idler gear, 25B ... 1st idler gear, 25C ... 2nd idler gear, 61 ... peripheral wall, 83 ... transmission room, 90 ... oil gutter, 91 ... Oil receiving part

Claims (6)

A transmission including an input shaft arranged parallel to each other , a counter shaft arranged below the input shaft, and an output shaft arranged coaxially with the input shaft.
A transmission case having a transmission chamber for accommodating the transmission, and
An automatic transmission provided with an oil gutter at the upper part of the transmission chamber, which receives the oil scraped up by the gear of the transmission and guides it to a part requiring lubrication.
The transmission has a reverse idler shaft provided with a reverse idler gear directly under the oil gutter.
The counter shaft is provided with a plurality of transmission gears including a first speed counter gear for a forward stage that meshes with the reverse idler gear.
The first-speed counter gear is the gear having the largest diameter among the plurality of transmission gears on the counter shaft, and is an automatic transmission characterized in that it is arranged behind the other transmission gears . The counter shaft transmits power to and from the output shaft so that the counter shaft always rotates when the vehicle is running.
The automatic transmission according to claim 1, wherein the reverse idler shaft transmits power to and from the counter shaft so as to always rotate when the vehicle is running. The reverse idler gear is
A first idler gear that meshes with the first speed counter gear arranged on the counter shaft,
It is composed of a second idler gear that meshes with the gear arranged on the input shaft.
The automatic transmission according to claim 1 or 2, wherein the first idler gear and the second idler gear are fixed to the reverse idler shaft adjacent to each other in the axial direction. The transmission case has a peripheral wall that surrounds the transmission from the outer peripheral side.
The oil gutter is placed close to the side of the peripheral wall,
The automatic transmission according to any one of claims 1 to 3, wherein the oil gutter has an oil receiving portion that receives oil on the side opposite to the peripheral wall. The input shaft is provided with a 1st speed input gear that meshes with the 1st speed counter gear and a reverse input gear adjacent to the 1st speed input gear.
The automatic transmission according to any one of claims 1 to 4, wherein the reverse input gear is formed to have a larger diameter than the first speed input gear. The automatic transmission according to claim 3, wherein the second idler gear is formed to have a larger diameter than the first idler gear.

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