JP2020003037A - Automatic transmission - Google Patents

Abstract

To provide an automatic transmission capable of improving lubrication performance without providing an oil pump.SOLUTION: In an automatic transmission 2, an oil gutter 90 is provided at an upper part in a transmission chamber 83, for receiving oil scraped up by a gear of a transmission 20 and guiding the oil 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. Then, a counter shaft 23 mutually transmits power between itself and an output shaft so as to always rotate during traveling of a vehicle, and the reverse idler shaft 25 transmits power between itself and the counter shaft 23 so as to always rotate during the traveling of the vehicle.SELECTED DRAWING: Figure 6

Description

  The present invention relates to an automatic transmission.

  Conventionally, in an automatic transmission mounted on a vehicle such as an automobile, the lubrication performance is improved by receiving oil scattered by being lifted up by rotation of a gear by an oil gutter and guiding the oil to a portion requiring lubrication. A known automatic transmission is known (see Patent Document 1). In addition, there is also known a transmission in which lubrication performance is improved by guiding oil to a portion requiring lubrication using an oil pump.

JP-A-60-215159

  However, the oil gutter 10 described in Patent Literature 1 uses the oil gutter 10 to remove the lubricating oil that is scooped up by the transmission gear 3 disposed on the drive shaft 2 disposed in the casing 1 and adheres to the inner wall 1a of the casing 1 to flow down. However, there was a problem in the collecting performance of the oil gutter 10. Further, with respect to a transmission provided with an 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 in view of the above circumstances, and has as its object to provide an automatic transmission that can improve lubrication performance without providing an oil pump.

  In order to achieve the above object, the present invention provides a transmission including an input shaft and a counter shaft arranged in parallel with each other, and an output shaft arranged coaxially with the input shaft, and a transmission for housing the transmission. A transmission case having a gearbox, and an oil gutter provided at an upper portion of the gearbox to receive the oil scooped up by the gears of the transmission and guide the oil to a portion requiring lubrication, The transmission has a reverse idler shaft provided with a reverse idler gear immediately below the oil gutter.

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

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

  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 houses the transmission. A transmission case having a transmission chamber, wherein an oil gutter is provided at an upper portion of the transmission chamber to receive oil guided by the gears of the transmission and guide the oil to a portion requiring lubrication, the automatic transmission comprising: The machine has a reverse idler shaft provided with a reverse idler gear immediately below the oil gutter. Thus, the automatic transmission according to one embodiment of the present invention can improve lubrication performance without providing an oil pump.

  Hereinafter, an 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 one embodiment of the present invention. 1 to 6, the up, down, front, rear, left and right directions are defined as the vehicle width direction being the left and right direction and the vehicle height direction being the up and down direction, when the traveling direction of the vehicle is the front and the retreating direction is the rear. Further, the width direction of the vehicle is also referred to as a vehicle width direction.

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

  The automatic transmission 2 includes a transmission case 4. 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. I have. The front end of the transmission case 4 is connected to the engine 3 by bolts (not shown). Of the transmission case 4, the front case 6, the rear case 7, and the extension case 8 excluding the torque converter housing 5 constitute a transmission case body 40. That is, the transmission case 4 includes the torque converter housing 5 and the transmission case main body 40.

  The automatic transmission 2 includes a shift unit 100, and the shift unit 100 is driven to perform a shift operation and a clutch operation of the automatic transmission 2. Here, the shift operation refers to an operation for switching the gear position of the automatic transmission 2, and the clutch operation refers to engaging (connecting) or releasing (disconnecting) the friction clutch 17 (see FIG. 3) of the automatic transmission 2. Operation.

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

  A pump impeller (not shown) is fixed to the inner surface of the shell 10B. A turbine runner (not shown) is installed inside the shell 10B so as to face the pump impeller, and the turbine runner is connected to the turbine shaft 11. A stator (not shown) is provided between the pump impeller and the turbine runner.

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

  A ring gear 10C is provided on the outer periphery of the shell 10B. The ring gear 10C transmits the rotation of the starter to the engine 3 when the pinion of the starter (not shown) is engaged when the engine 3 is started.

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

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

  An oil pump 12 is housed in the torque converter housing 5, and the oil pump 12 is formed of, for example, a trochoid type oil pump. The oil pump 12 includes a pump housing 12A. The pump housing 12A includes a second pump housing 14 fixed to the partition wall 55 by bolts (not shown) and a first pump fastened to the second pump housing 14 by bolts (not shown). And 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 radially outward of the inner rotor, and rotates with the rotation of the inner rotor. The trochoidal oil pump 12 forms an operating chamber (not shown) for accommodating oil between the external teeth and the internal teeth when the internal teeth formed on the outer rotor and the external teeth formed on the inner rotor come into contact with each other. .

  When the power of the engine 3 is transmitted to the inner rotor via the front cover 10A, in the oil pump 12, the inner rotor and the outer rotor rotate in one direction. At this time, as the volume of the working chamber increases and decreases continuously, 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 a rear end portion of the turbine shaft 11, and the flange portion 11A is formed to have a larger diameter than a front end portion and a central portion of the turbine shaft 11. An annular flywheel 16 is attached to the flange 11A. The flywheel 16 is a friction engagement 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 surrounding the friction clutch 17 and the transmission 20 from an outer peripheral side, a clutch chamber 82 in which the friction clutch 17 is accommodated, and a transmission chamber 83 in which the transmission 20 is accommodated. And a partition 65 for partitioning into two.

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

  The friction clutch 17 is mounted near the front end 21a of the input shaft 21 in the axial direction. The input shaft 21 is housed in the front case 6 and the rear case 7, and is rotatably supported on the flange 11A via a bearing 38B at a front end 21a in the axial direction, and the output shaft 22 at a rear end 21b in the axial direction. It is supported rotatably.

  The output shaft 22 is disposed 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 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 disk 17A provided 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 disk 17A against the flywheel 16, and a pressure plate 17B. And a diaphragm spring 17C biasing the flywheel 16 side.

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

  A release bearing 18 is provided on the outer peripheral portion of the cylindrical 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 and contacts and separates radially inward of the diaphragm spring 17C.

  When the release bearing 18 is moved forward in the axial direction of the input shaft 21 by the release lever 19, the release bearing 18 presses the radially inner end 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 crankshaft of the engine 3 is not transmitted to the input shaft 21.

  When the release bearing 18 is moved rearward in the axial direction of the input shaft 21 by the release lever 19, the release bearing 18 separates from the radially inner end of the diaphragm spring 17C. At this time, the rotation of the flywheel 16 (the rotation of the crankshaft of the engine 3 via the torque converter 10) is applied to the input shaft by the diaphragm spring 17C urging the pressure plate 17B to press the clutch disk 17A against the flywheel 16. 21. As described above, the friction clutch 17 switches the power transmission state between the crankshaft of the engine 3 and the input shaft 21 to the transmission state or the cutoff state.

  A 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 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 fourth-speed input gear 24A, a third-speed input gear 24B, a second-speed input gear 24C, a first-speed input gear 24D, and a reverse input gear 24E from the friction clutch 17 toward the output shaft 22. .

  The fourth-speed input gear 24A, the third-speed input gear 24B, the second-speed input gear 24C, the first-speed input gear 24D, and the reverse input gear 24E are relatively rotatably connected to the input shaft 21.

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

  The counter shaft 23 is provided with a fourth speed counter gear 26A, a third speed counter gear 26B, a second speed counter gear 26C, a first speed counter gear 26D, and a counter drive gear 26E from the friction clutch 17 side toward the output shaft 22. .

  The fourth-speed counter gear 26A, the third-speed counter gear 26B, the second-speed counter gear 26C, the first-speed counter gear 26D, and the counter drive gear 26E are fixed to the counter shaft 23.

  The fourth-speed counter gear 26A, the third-speed counter gear 26B, the second-speed counter gear 26C, and the first-speed counter gear 26D are respectively a fourth-speed input gear 24A, a third-speed input gear 24B, and a second-speed input gear 24C that constitute the same shift speed. , Is engaged with the first 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 accommodate a synchronizer 28 for the third and fourth speeds, a synchronizer 29 for the first and second speeds, and a synchronizer 30 for the reverse fifth and fifth speeds.

  The third-speed / fourth-speed synchronizer 28 is provided so as to be rotatable integrally with the input shaft 21 and to be movable in the axial direction of the input shaft 21. When the shift-and-select shaft 33 is operated, the third-speed / fourth-speed synchronizer 28 controls the input shaft 21 via the third-speed / fourth-speed shift shaft, shift yoke, and shift fork (not shown). It is moved in the axial direction.

  The first-speed / second-speed synchronizer 29 is rotatable integrally with the input shaft 21 and is provided movably in the axial direction of the input shaft 21. When the shift-and-select shaft 33 is operated, the first-second-speed synchronizer 29 is connected to the input shaft 21 via a first-second-speed shift shaft, a shift yoke, and a shift fork (not shown). It is moved in the axial direction.

  The synchronous device 30 for the reverse fifth speed is provided so as to be rotatable integrally with the input shaft 21 and to be movable in the axial direction of the input shaft 21. When the shift-and-select shaft 33 is operated, the synchronizer 30 for the reverse fifth speed shifts in the axial direction of the input shaft 21 via a shift shaft, a shift yoke, and a shift fork (not shown). Moved to

  The third-speed / fourth-speed synchronizer 28 connects the fourth-speed input gear 24A to the input shaft 21 by moving from the neutral position to the front side in the axial direction of the input shaft 21 to establish the fourth forward speed. The power of the input shaft 21 is transmitted to the counter shaft 23 via the fourth speed input gear 24A and the fourth 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, a drive shaft, and a drive rear wheel (not shown) are connected to the output shaft 22 via a propeller shaft (not shown).

  Thereby, the power transmitted to the output shaft 22 is transmitted to the differential device via the propeller shaft, and then is 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 runs.

  The third-speed / fourth-speed synchronizer 28 moves the neutral position to the rear side in the axial direction of the input shaft 21 to connect the third-speed input gear 24B to the input shaft 21 to establish the third forward speed. The power of the input shaft 21 is transmitted to the counter shaft 23 via the third speed input gear 24B and the third speed counter gear 26B.

  The first-second-speed synchronizer 29 moves from the neutral position to the front side in the axial direction of the input shaft 21 to connect the second-speed input gear 24C to the input shaft 21 to establish the second forward speed. 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 first-gear second-speed synchronizer 29 connects the first-gear input gear 24D 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 the first forward gear. The power of the input shaft 21 is transmitted to the counter shaft 23 via the first speed input gear 24D and the first speed counter gear 26D.

  The reverse fifth gear synchronizer 30 moves the neutral position to the front side in the axial direction of the input shaft 21, thereby connecting the reverse input gear 24 </ b> E to the input shaft 21 to establish a reverse gear. Power is transmitted from the reverse input gear 24E to the counter shaft 23 via a later-described reverse idler gear 25A (see FIG. 5, a first idler gear 25B, a second idler gear 25C) and a first-speed counter gear 26D. 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 moves backward.

  The reverse fifth speed synchronizing device 30 connects the fifth speed clutch gear 22A 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 the fifth forward speed. The power of the input shaft 21 is directly transmitted to the output shaft 22.

  The shift case 9 is provided above the front case 6, and the 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 direction in which the input shaft 21 extends.

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

  An oil pan 41 is attached to a 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. A valve body 42 is accommodated between the oil pan 41 and the lower part of the front case 6, and the valve body 42 is fastened to the lower part of the front case 6 by bolts (not shown).

  The valve body 42 supplies the oil sucked 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 lock-up clutch (not shown) of the torque converter 10, or as oil flowing from the pump impeller to the turbine runner.

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

  The release lever 19 is disposed 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 swing fulcrum, and an end of the release lever 19 connected to the shift unit 100 has one end in the axial direction. , The end on the release bearing 18 side moves to the other end in the axial direction. The release lever 19 forms a release member in the present invention.

  More specifically, the release lever 19 is swingably supported by the partition wall 65 of the front case 6 at the swing center. 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 that transmits the operating force of the shift unit 100 to the release bearing 18 is as follows. The release lever 19 is not limited. For example, a member that transmits the operating force of the shift unit 100 to the release bearing 18 without swinging movement can be used as the release member.

  In FIG. 4, the front case 6 has a valve body chamber 84 above the oil storage chamber 43 that houses the valve body 42 continuously with the oil storage chamber 43, and separates the clutch chamber 82 and the valve body chamber 84. It has a ceiling wall 68. A rear end of the ceiling wall 68 is connected to a lower portion of the partition wall 65, a right end of the ceiling wall 68 is connected to a lower right portion of the peripheral wall 61, and a left end of the ceiling wall 68 is connected to a lower end of a vertical wall 69 described later. 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 the present embodiment, the automatic transmission 2 includes 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. And a transmission case 4 having a transmission chamber 83 for accommodating the transmission 20.

  Further, an oil gutter 90 is provided at an upper portion in the transmission chamber 83 to receive the oil scooped up by the gears of the transmission 20 and guide the oil 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 below the oil gutter 90. The counter shaft 23 transmits power to and from the output shaft 22 so that the counter shaft 23 always rotates when the vehicle travels. The reverse idler shaft 25 rotates the counter shaft 23 so that it always rotates when the vehicle travels. Power is transmitted to and from each other. That is, in the present embodiment, the output shaft 22 is configured to always rotate when the vehicle travels, and the reverse idler shaft 25 is connected to the counter shaft 23 so as to always rotate when the output shaft 22 rotates. The output shaft 22 is engaged.

  As shown in FIG. 5, the reverse idler shaft 25 has a front end rotatably supported by a partition 65 of the front case 6 and a rear end thereof by a partition 75 of the rear case 7 via bearings. In detail, the front end of the reverse idler shaft 25 is formed on a rear surface (vertical wall facing rearward) of a bulging portion 65A bulging rearward from the partition wall 65 of the front case 6 via a bearing 25D. It is supported by a shaft through a bearing 25D. The rear end of the reverse idler shaft 25 is supported by a bearing holding portion formed on a partition 75 of the rear case 7 via a bearing 25E. The bulging portion 65A bulges rearward from the partition wall 65 to near the mating surface of the front case 6 and the rear case 7 in the axial direction. The reverse idler gear 25A includes a first idler gear 25B meshing with a gear (first-speed counter gear 26D) arranged on the counter shaft 23 and a second idler gear meshing with a gear (reverse input gear 24E) arranged on the input shaft 21. 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 has a larger diameter than the first idler gear 25B, the outer peripheral edge of the second idler gear 25C is disposed so as to overlap the outer peripheral edge of the first-speed counter gear 26D when viewed in the axial direction. ing. That is, the outer peripheral edge of the second idler gear 25C is located behind the meshing position of the first speed counter gear 26D and the first idler gear 25B. Note that FIG. 5 is a vertical section passing through the axis of the reverse idler gear 25A, and therefore, in FIG. 5, the gears 26B, 26C, and 26D of the counter shaft 23 are only a part thereof.

  The transmission case 4 has peripheral walls 61 and 71 that surround the transmission 20 from the outer peripheral side. An oil gutter 90 is arranged on the side of the peripheral walls 61 and 71 and close to 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. With respect to 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 above the reverse idler gear 25A where the interference is a problem is set to a height that is closer to receiving the oil scattered by the reverse idler gear 25A while securing a gap with the reverse idler gear 25A. ing. The front portion where the reverse idler gear 25A does not exist has a bottom surface set at a position lower than the upper position of the reverse idler gear 25A, so that the internal space of the oil gutter 90 is enlarged to increase the oil capacity, and the front of the oil. Is causing the flow to.

  As shown in FIG. 6, the oil gutter 90 has an oil receiving portion 91 that receives oil on the side (left side) opposite to the peripheral wall 61. The oil receiving portion 91 extends leftward from the upper end of the left wall of the oil gutter 90 and extends above the input shaft 21. More specifically, the oil receiving portion 91 is disposed above a shift shaft disposed above the input shaft 21, and is formed so as to extend obliquely upward and to the left from the oil gutter 90. The oil receiving portion 91 receives the oil scattered in the transmission chamber 83 and guides it to the oil gutter 90, and also collects the oil scooped up by the reverse idler gear 25A and jumped over the oil gutter 90.

  The oil gutter 90 drops oil on the upper surface 65B of the bulging portion 65A so as to supply the 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 to descend downward, the oil dropped 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. To reach the bearing 25D. A groove for guiding the flow of the 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 stores excess oil in the transmission chamber 83. The stirring resistance of the transmission can be reduced, and the fuel economy performance of the vehicle can be improved.

  As shown in FIG. 6, the counter shaft 23 is disposed slightly below and to the right of 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 height of the input shaft 21 and the output shaft 22 and is disposed on the right side in the transmission room 83. The oil gutter 90 is disposed on the upper right side in the transmission chamber 83 near the peripheral walls 61 and 71, and is disposed slightly above the reverse idler shaft 25.

  As shown in FIG. 6, in the present embodiment, the rotation direction of each shaft at the time of forward movement is such that the input shaft 21 is counterclockwise (counterclockwise), the counter shaft 23 is clockwise (clockwise), and the reverse idler shaft. 25 is counterclockwise (counterclockwise).

  The power transmission path of the reverse stage includes the input shaft 21, the synchronizer 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. is there.

  The first-speed counter gear 26D of the counter shaft 23 is the largest-diameter gear among the transmission gears on the counter shaft 23, and is disposed behind other transmission gears. Therefore, the oil accumulated at 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. Referring to FIG. 6, in the present embodiment, during forward movement, the first-speed counter gear 26D rotates clockwise (clockwise) with a large amount of oil. The first-speed counter gear 26D meshes with the first-speed input gear 24D before the first idler gear 25B, and the oil on the tooth surface flows out in the axial direction (front-rear direction) by meshing with the first-speed input gear 24D. However, since the first idler gear 25B has a small diameter, the synchronizer 29 and the reverse input gear 24E exist before and after the meshing portion, and the oil flowing out in the axial direction (front-back direction) is transmitted to the synchronizer 29 and the reverse input gear 24E. It can be guided to reach the reverse idler gear 25A.

  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, so that the oil supplied by the first-speed counter gear 26D can be further reduced. You can receive more. Further, the second idler gear 25C has its outer periphery close to the peripheral wall 61 of the transmission case 4 and, as shown in FIG. 5, the peripheral wall 61 is lower toward the outer periphery of the second idler gear 25C. Since the oil is formed on the slope, the oil supplied by the first-speed counter gear 26D can be scraped up more. In FIG. 6, the reverse idler shaft 25 is counterclockwise (counterclockwise) when the vehicle advances, and the reverse idler gear 25A can form an oil flow flowing upward along the peripheral wall 71. This oil flow is guided by the right wall and the peripheral wall 71 of the oil gutter 90, passes between the right wall and the peripheral wall 71 of the oil gutter 90, and reaches above the oil gutter 90. Since the inner surface of the transmission case 4 located above the oil gutter 90 is bent from the peripheral wall 71 for guiding the oil and is formed substantially horizontally, the flow of the oil is stagnated at this portion, and the retained oil is moved downward. And falls into the oil gutter 90 and the oil receiving portion 91, and is supplied into the oil gutter 90.

  Next, effects 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 in parallel with each other, and an output shaft 22 arranged coaxially with the input shaft 21. The transmission case 4 has a transmission room 83 in which the transmission 20 is housed. An oil gutter 90 is provided at an upper portion in the transmission chamber 83 to receive the oil scooped up by the gears of the transmission 20 and guide the oil 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.

  Thus, since the reverse idler gear 25A is disposed immediately below 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 gear again. Since the oil can be supplied to the gear 25A, the lubrication performance of the reverse idler gear 25A can be improved. As a result, lubrication performance can be improved without providing an oil pump.

  Further, in the present embodiment, the counter shaft 23 transmits power to and from the output shaft 22 so that the counter shaft 23 always rotates when the vehicle travels, and the reverse idler shaft 25 constantly rotates when the vehicle 1 travels. Power is transmitted to and from the counter shaft 23 in such a manner.

  This increases the chance that the reverse idler gear 25A of the reverse idler shaft 25 rotates, so that more oil can be supplied to the oil gutter 90 and 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 backward running but also during forward running.

  The reverse idler gear 25A is composed of a first idler gear 25B meshing with a gear arranged on the counter shaft 23 and a second idler gear 25C meshing 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 so as to be adjacent to each other in the axial direction.

  Thus, by rotating the adjacent first idler gear 25B and second idler gear 25C, 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 that surround the transmission 20 from the outer peripheral side, and an oil gutter 90 is disposed adjacent to the side 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.

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

  While embodiments of the present invention have been disclosed, it will be apparent that modifications may be made by those skilled in the art 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 ... first idler gear, 25C ... second idler gear, 61 ... peripheral wall, 83 ... transmission room, 90 ... oil gutter, 91 ... Oil receiver

Claims (4)

A transmission including an input shaft and a counter shaft arranged in parallel with each other, and an output shaft arranged coaxially with the input shaft;
A transmission case having a transmission room for housing the transmission,
An automatic transmission in which an oil gutter is provided at an upper portion of the transmission chamber to receive oil scooped up by gears of the transmission and guide the oil to a portion requiring lubrication,
The automatic transmission according to claim 1, wherein the transmission has a reverse idler shaft provided with a reverse idler gear immediately below the oil gutter. The counter shaft is mutually transmitting power between the output shaft and the output shaft so that the counter shaft always rotates during traveling of the vehicle,
2. The automatic transmission according to claim 1, wherein the reverse idler shaft transmits power to and from the counter shaft such that the reverse idler shaft always rotates during traveling of the vehicle. 3. The reverse idler gear,
A first idler gear meshing with a gear disposed on the counter shaft;
A second idler gear meshing with a gear disposed on the input shaft,
3. The automatic transmission according to claim 1, wherein the first idler gear and the second idler gear are fixed adjacent to the reverse idler shaft in an axial direction. 4. The transmission case has a peripheral wall surrounding the transmission from an outer peripheral side,
The oil gutter is arranged near the side of the peripheral wall,
4. The automatic transmission according to claim 1, wherein the oil gutter has an oil receiving portion that receives oil on a side opposite to the peripheral wall. 5.

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