JP7363250B2 - Vehicle transmission - Google Patents

Description

The present invention relates to a vehicle transmission.

An automatic transmission described in Patent Document 1 is known as a transmission equipped with a transfer device. This automatic transmission has an input shaft that transmits engine power, a main shaft that is installed coaxially with the input shaft, and a main shaft that transmits power from the input shaft, and a main shaft that is installed coaxially with the main shaft and that is installed coaxially with the input shaft. It has a rear output shaft to which power is transmitted.

Furthermore, the automatic transmission includes a counter shaft that is installed parallel to the main shaft and the rear output shaft and connected to the main shaft via multiple gear pairs, and a counter shaft that is installed parallel to the rear output shaft and transfers from the front output shaft. It has a front output shaft to which power is transmitted via a chain.

The rear output shaft transmits engine power to the rear wheels, and the front output shaft transmits engine power to the front wheels.

Patent No. 3982119

In such conventional automatic transmissions, the countershaft is installed parallel to the main shaft, and the countershaft is connected to the main shaft via multiple gear pairs, so the transmission is caused by the meshing of the gear pairs. There is a risk that the distance between the main shaft and the counter shaft will increase due to the repulsive force, and there is a risk that the main shaft and the counter shaft will be deflected, so there is still room for improvement.

For this reason, if the oil pump is driven by a counter shaft or main shaft, there is a risk that the axis of the oil pump may be misaligned and the oil pump may not rotate smoothly, which may deteriorate the suction efficiency and durability of the oil pump. There is.

The present invention has been made in view of the above-mentioned circumstances, and is an object for use in vehicles that can increase the rigidity of the pump accommodating portion that accommodates the oil pump and prevent deterioration of the suction efficiency and durability of the oil pump. The purpose is to provide a transmission.

The present invention includes a first rotating shaft to which power is transmitted from a drive source, the first rotating shaft being provided coaxially with the first rotating shaft, and an axial end thereof being an axial end of the first rotating shaft. a second rotating shaft that is relatively rotatably connected to the rotating shaft, and a plurality of rotating shafts that are installed parallel to the first rotating shaft and the second rotating shaft, a third rotating shaft connected via a gear pair; a fourth rotating shaft installed parallel to the first rotating shaft, the second rotating shaft, and the third rotating shaft; a chain that is wrapped around the second rotating shaft and the fourth rotating shaft and transmits the power of the second rotating shaft to the fourth rotating shaft; and an oil pump that is driven by the third rotating shaft. , a transmission case that accommodates the first rotation shaft, the second rotation shaft, the third rotation shaft, and the fourth rotation shaft, the transmission case housing the third rotation shaft The vertical wall includes a first flat wall and a vertical wall located rearward of the first flat wall and connected to the first flat wall through a step. and a second flat wall portion connected to each other, and a cylindrical bearing support portion that rotatably supports the second rotating shaft via a bearing is provided on the second flat wall portion. A pump accommodating portion for accommodating the oil pump is provided in the first flat wall portion and the second flat wall portion, and the pump accommodating portion is provided in the first flat wall portion and the second flat wall portion. straddles the second flat wall portion and bulges rearward than the second flat wall portion in the axial direction of the third rotating shaft, and when viewed from the axial direction of the third rotating shaft, the The third rotating shaft is installed between the second rotating shaft and the fourth rotating shaft, and the axis thereof is located within a region surrounded by the chain, and the pump accommodating portion is located between the second rotating shaft and the fourth rotating shaft. It is characterized in that it is connected to a bearing support part.

As described above, according to the present invention, the rigidity of the pump accommodating portion that accommodates the oil pump can be increased, and deterioration of the suction efficiency and durability of the oil pump can be prevented.

FIG. 1 is a left side view of a vehicle transmission according to an embodiment of the present invention. FIG. 2 is a rear view of a transfer rear case of a vehicle transmission according to an embodiment of the present invention. FIG. 3 is a view of a transfer rear case of a vehicle transmission according to an embodiment of the present invention, viewed diagonally from the rear left. FIG. 4 is a diagram of a transfer rear case of a vehicle transmission according to an embodiment of the present invention, viewed diagonally from the front right. FIG. 5 is a view of the transfer case seen from the VV direction in FIG. FIG. 6 is a cross-sectional view of the vehicle transmission taken along the VI-VI direction in FIG. FIG. 7 is a diagram showing a positional relationship among a rear output shaft, a counter shaft, and a front output shaft of a vehicle transmission according to an embodiment of the present invention.

A vehicle transmission according to an embodiment of the present invention includes a first rotating shaft to which power is transmitted from a drive source, and is provided coaxially with the first rotating shaft, and an end portion in the axial direction is provided on the same axis as the first rotating shaft. a second rotating shaft that is relatively rotatably connected to the axial end of the rotating shaft; and a second rotating shaft that is installed parallel to the first rotating shaft and the second rotating shaft; a third rotating shaft connected to the rotating shaft via a plurality of gear pairs; a fourth rotating shaft installed parallel to the first rotating shaft, the second rotating shaft, and the third rotating shaft; a chain that is wrapped around the second rotating shaft and the fourth rotating shaft and transmits the power of the second rotating shaft to the fourth rotating shaft; an oil pump that is driven by the third rotating shaft; a transmission case that accommodates a rotating shaft, a second rotating shaft, a third rotating shaft, and a fourth rotating shaft, the transmission case having a vertical wall located behind the third rotating shaft. The vertical wall is provided with a pump accommodating part for accommodating the oil pump, and a cylindrical bearing support part for rotatably supporting the second rotating shaft via a bearing. When viewed from the axial direction, the third rotating shaft is installed between the second rotating shaft and the fourth rotating shaft, and its axial center is located within the area surrounded by the chain, and the third rotating shaft is located within the area surrounded by the chain. The portion is connected to the bearing support portion.

As a result, the vehicle transmission according to the embodiment of the present invention can increase the rigidity of the pump accommodating portion that accommodates the oil pump, and can prevent the suction efficiency and durability of the oil pump from deteriorating.

DESCRIPTION OF THE PREFERRED EMBODIMENTS A vehicle transmission according to an embodiment of the present invention will be described below with reference to the drawings.
1 to 7 are diagrams showing a vehicle transmission according to an embodiment of the present invention. 1 to 7, the up, down, front, back, left, and right directions are defined as the forward direction in which the vehicle equipped with the vehicle transmission is mounted, and the rear direction in the backward direction. The horizontal direction is the vertical direction.

First, the configuration will be explained.
In FIG. 1, a vehicle 1 is equipped with an automatic transmission 2, and the automatic transmission 2 is installed vertically below a floor panel 1A of the vehicle 1 while being connected to an engine 3. The automatic transmission 2 of this embodiment constitutes the vehicle transmission of the present invention, and the engine 3 constitutes the drive source of the present invention.

The automatic transmission 2 includes a transmission case 4, and the transmission case 4 includes a torque converter housing (hereinafter simply referred to as torque converter housing) 5, a front case 6, a transfer front case 7, and a transfer rear case 8. It is composed of:

An engine 3 serving as an internal combustion engine is connected to the front end of the torque converter housing 5 by a bolt (not shown). The engine 3 burns fuel and converts thermal energy into mechanical energy.

The torque converter housing 5 accommodates a torque converter (not shown). The torque converter amplifies and outputs the power of the engine 3. As shown in FIG. 6, the transmission case 4 accommodates an input shaft 10, a rear output shaft 11, a counter shaft 12, and a front output shaft 13.

The input shaft 10 extends in the front-rear direction, and power from the engine 3 is transmitted to the input shaft 10 via a torque converter.

The rear output shaft 11 faces the input shaft 10 in the axial direction (front-rear direction) of the input shaft 10 and is provided coaxially with the input shaft 10 . The rear end 10a of the input shaft 10 is rotatably connected to the front end 11a of the rear output shaft 11 via a needle bearing 14A.

Thereby, the rear output shaft 11 is relatively rotatably connected to the input shaft 10. The rear end portion 10a of the input shaft 10 of this embodiment constitutes the axial end portion of the first rotating shaft of the present invention, and the front end portion 11a of the rear output shaft 11 constitutes the second rotating shaft of the present invention. It constitutes the axial end of the shaft.

The counter shaft 12 is installed parallel to the input shaft 10 and the rear output shaft 11, and the front output shaft 13 is installed parallel to the input shaft 10, the rear output shaft 11, and the counter shaft 12.
The input shaft 10 of this embodiment constitutes the first rotating shaft of the present invention, and the rear output shaft 11 constitutes the second rotating shaft of the present invention. The counter shaft 12 constitutes the third rotating shaft of the present invention, and the front output shaft 13 constitutes the fourth rotating shaft of the present invention.

As shown in FIG. 6, a partition 7A is provided at the rear of the transfer front case 7, and a rear joint 7a is formed at the rear end of the partition 7A.

As shown in FIGS. 2 and 3, the transfer case 8 includes a peripheral wall 8A, an annular flange portion 8B provided at the front end of the peripheral wall 8A and protruding radially outward from the peripheral wall 8A, and a rear portion of the peripheral wall 8A. and a rear wall 8C extending radially inward from the peripheral wall 8A. The rear wall 8C of this embodiment constitutes the vertical wall of the present invention.

The transfer front case 7 and the transfer rear case 8 are integrated by joining the flange portion 8B to the rear joint portion 7a of the transfer front case 7 with bolts (not shown).

As shown in FIG. 6, the partition wall 7A is provided with cylindrical bearing supports 31, 32, 33, and the transfer case 8 is provided with cylindrical bearing supports 34, 35.

The front end portion 11a of the rear output shaft 11 is rotatably supported on the bearing support portion 31 via a ball bearing 14B, and the rear side of the rear output shaft 11 is rotatably supported on the bearing support portion 34 via a ball bearing 14C. It is rotatably supported.

A rear end portion 12a of the counter shaft 12 is rotatably supported by the bearing support portion 32 via a ball bearing 14D.

The front side of the front output shaft 13 is rotatably supported by the bearing support portion 33 via a ball bearing 14E, and the rear end portion 13a of the front output shaft 13 is rotatably supported by the bearing support portion 35 via a ball bearing 14F. freely supported.

The bearing support part 34 of this embodiment constitutes the first bearing support part of the present invention, and the bearing support part 35 constitutes the second bearing support part of the present invention. The ball bearings 14C and 14F constitute the bearing of the present invention.

As shown in FIG. 2, the bearing support portion 34 is connected to the rear wall 8C via a circular recess 34A, and the recess 34A bulges forward from the rear wall 8C.

As shown in FIG. 6, the input shaft 10 is provided with a first input gear 15A, a second input gear 15B, and a third input gear 15C from the front side to the rear side.

The first input gear 15A, the second input gear 15B, and the third input gear 15C are rotatable relative to the input shaft 10.

The counter shaft 12 is provided with a first counter gear 16A, a second counter gear 16B, a third counter gear 16C, and a counter drive gear 16D from the front side to the rear side.

The first counter gear 16A, the second counter gear 16B, and the third counter gear 16C are spline-fitted to the counter shaft 12 and rotate integrally with the counter shaft 12. The counter drive gear 16D is fixed to the counter shaft 12 and rotates integrally with the counter shaft 12.

The first counter gear 16A, the second counter gear 16B, and the third counter gear 16C mesh with the first input gear 15A, the second input gear 15B, and the third input gear 15C, respectively.

A clutch gear 17 and a counter driven gear 18 are provided on the rear output shaft 11. The counter driven gear 18 is fixed to the rear output shaft 11 and rotates integrally with the rear output shaft 11. Counter driven gear 18 meshes with counter drive gear 16D.

A clutch gear 17 is spline-fitted to the counter driven gear 18, and the clutch gear 17 is composed of a dog and rotates together with the counter driven gear 18.

The input shaft 10 is provided with synchronizers 19 and 22. The synchronizers 19, 22 each have a hub 19A, 22A, a sleeve 19B, 22B and a synchronizer ring 19C, 19D, 22C, 22D.

The hubs 19A and 22A are spline-fitted to the input shaft 10 and rotate together with the input shaft 10. The sleeve 19B is provided to be movable in the axial direction of the input shaft 10, and can fit the hub 19A to the first input gear 15A or the second input gear 15B via the synchronizer ring 19C or the synchronizer ring 19D. This synchronizes the rotation of the input shaft 10 and the first input gear 15A, or the rotation of the input shaft 10 and the second input gear 15B.

The sleeve 22B is provided so as to be movable in the axial direction of the input shaft 10, and by fitting the hub 22A to the third input gear 15C or the clutch gear 17 via the synchronizer ring 22C or synchronizer ring 22D, the input shaft 10 can be moved freely. The rotations of the shaft 10 and the third input gear 15C, or the rotations of the input shaft 10 and the clutch gear 17 (rear output shaft 11) are synchronized.

The first input gear 15A and the first counter gear 16A of this embodiment constitute a gear pair of the present invention, and the second input gear 15B and the second counter gear 16B constitute a gear pair of the present invention. do. The third input gear 15C and the third counter gear 16C constitute a gear pair of the present invention, and the counter drive gear 16D, the clutch gear 17, and the counter driven gear 18 constitute a gear pair of the present invention.

The synchronizer 19 is movable by a shift and select shaft (not shown) via a shift fork 20, a shifter shaft 21, and a shift yoke 21A (see FIG. 7).

Specifically, the shift fork 20 is fitted into the sleeve 19B. The shifter shaft 21 extends parallel to the input shaft 10 and is movable in the axial direction of the input shaft 10. The shift fork 20 is attached to a shifter shaft 21, and when the shifter shaft 21 moves in the axial direction, it moves in the axial direction of the input shaft 10 and moves the sleeve 19B in the axial direction of the input shaft 10.

For example, when the synchronizer 19 is composed of a synchronizer 19 for 3rd and 4th gears, the shift and select axis selects the shift yoke 21A for 3rd and 4th gears, and When the shift fork 20 for the third and fourth speed stages is moved in the axial direction of the input shaft 10 via the shifter shaft 21 for the stages, the sleeve 19B is moved in the axial direction of the input shaft 10.

When the sleeve 19B moves from the neutral position to the front side in the axial direction of the input shaft 10, the first input gear 15A for the third gear is connected to the input shaft 10 via the hub 19A to establish the third forward gear. , transmits the power of the input shaft 10 to the counter shaft 12 via the first input gear 15A and the first counter gear 16A.

The power transmitted to the counter shaft 12 is transmitted from the counter drive gear 16D to the rear output shaft 11 via the counter driven gear 18. A rear differential device, a rear drive shaft, and a driving rear wheel (all not shown) are connected to the rear output shaft 11 via a rear propeller shaft (not shown).

As a result, the power transmitted to the rear output shaft 11 is transmitted to the rear differential device via the rear propeller shaft, distributed to the left and right rear drive shafts by the rear differential device, and then transmitted to the driving rear wheels. . As a result, the vehicle 1 is driven.

On the other hand, when the sleeve 19B moves from the neutral position to the rear side in the axial direction of the input shaft 10, the second input gear 15B for the 4th gear is connected to the input shaft 10 via the hub 19A, and the 4th forward gear is connected to the input shaft 10 via the hub 19A. is established, and the power of the input shaft 10 is transmitted to the counter shaft 12 via the second input gear 15B and the second counter gear 16B.

The synchronizer 22 is movable by a shift and select shaft (not shown) via a shift fork 23 that fits into the sleeve 22B, a shifter shaft 24, and a shift yoke 24A (see FIG. 7). A description of the operation of the synchronizer 22 will be omitted.

A transfer drive sprocket 36 is provided on the rear output shaft 11 so as to be relatively rotatable. A transfer synchronizer 37 for switching between two-wheel drive and four-wheel drive is installed on the rear output shaft 11. Transfer synchronizer 37 includes a hub 37A, a sleeve 37B, and a synchronizer ring 37C.

The hub 37A is spline-fitted to the rear output shaft 11 and rotates together with the rear output shaft 11. The sleeve 37B is provided to be movable in the axial direction of the rear output shaft 11, and by fitting the hub 37A to the transfer drive sprocket 36 via the synchronizer ring 37C, the sleeve 37B connects the rear output shaft 11 and the transfer drive sprocket. Synchronize the rotation with 36.

In the transfer synchronizer 37, when the sleeve 37B moves forward, the transfer drive sprocket 36 is connected to the rear output shaft 11 via the hub 37A and rotates together with the rear output shaft 11.

On the other hand, when the sleeve 37B moves rearward, the transfer drive sprocket 36 and the rear output shaft 11 rotate relative to each other.

A transfer driven sprocket 38 is provided on the front output shaft 13, and the transfer driven sprocket 38 rotates together with the front output shaft 13. Transfer driven sprocket 38 is connected to transfer drive sprocket 36 via chain 39.

As shown in FIG. 1, a transfer actuator 40 is provided at the top of the transfer case 8.

The transfer actuator 40 moves the sleeve 37B to the rear side by hydraulically operating an operating shaft (not shown) via a shifter shaft that moves in the front-back direction by the operating shaft and a shift fork 40A (see FIG. 6) attached to the shifter shaft. It is moved in the axial direction of the output shaft 11. Shift fork 40A is fitted into sleeve 37B.

As shown in FIG. 6, when the sleeve 37B is moved forward from the neutral position by the operating shaft, the sleeve 37B becomes the four-wheel drive position, the transfer drive sprocket 36 is connected to the rear output shaft 11, and the rear output shaft 11 is connected to the transfer drive sprocket 36. It rotates as one.

At this time, the power of the rear output shaft 11 is transmitted to the front output shaft 13 via the transfer drive sprocket 36, the chain 39, and the transfer driven sprocket 38. The front output shaft 13 is connected to a front differential device, a front drive shaft, and a driving front wheel (all not shown) via a front propeller shaft (not shown).

As a result, the power of the engine 3 transmitted to the rear output shaft 11 is transmitted to the driving rear wheels via the rear propeller shaft, etc., and is also transmitted from the front output shaft 13 to the front propeller shaft, the front differential device, and the left and right front wheels. The signal is transmitted to the left and right front wheels via the drive shaft, and the vehicle 1 is driven by the front and rear wheels. That is, the vehicle 1 is driven by four wheels.

On the other hand, when the operating shaft is in the front position and the vehicle 1 is in the four-wheel drive position, when the transfer actuator 40 operates the operating shaft to move the sleeve 37B from the four-wheel drive position to the rear side, The connection between the transfer drive sprocket 36 and the rear output shaft 11 is released, and the transfer drive sprocket 36 rotates relative to the rear output shaft 11.

At this time, power is no longer transmitted from the rear output shaft 11 to the transfer drive sprocket 36, and power from the rear output shaft 11 is not transmitted to the front output shaft 13. As a result, the power of the engine 3 is transmitted only to the driving rear wheels, and the vehicle 1 becomes two-wheel drive.

A shifter shaft operated by the operating shaft of the transfer actuator 40 extends from the inside of the frame 50 to the transfer case 8, and is slidably supported by the partition wall 7A and the rear wall 8C.

The automatic transmission 2 of this embodiment accommodates a rear output shaft 11, a front output shaft 13, a transfer synchronizer 37, and a chain 39; A transfer device is constituted by the transfer case 8 and the transfer case 8. That is, the automatic transmission 2 of this embodiment is an automatic transmission equipped with a transfer device.

As shown in FIG. 7, when viewed from the axial direction of the counter shaft 12, the counter shaft 12 is installed between the rear output shaft 11 and the front output shaft 13, and the shaft center O1 is surrounded by the chain 39. located within the area covered by

Specifically, the counter shaft 12 is installed at a lower position than the rear output shaft 11, and the front output shaft 13 is installed at a lower position than the counter shaft 12. When viewed from the axial direction of the counter shaft 12, the counter shaft 12, the rear output shaft 11, and the front output shaft 13 have their respective shaft centers O1, O2, and O3 on the virtual straight line L. They are set up so that they are lined up.

As shown in FIG. 6, an oil pump 41 is connected to the rear end 12a of the counter shaft 12.

The oil pump 41 includes a trochoidal pump body 42 and a drive shaft 43 that connects the pump body 42 and the rear end portion 12 a of the counter shaft 12 .

The pump body 42 has an inner rotor 42A and an outer rotor 42B. A drive shaft 43 is connected to the inner rotor 42A, and the inner rotor 42A rotates integrally with the drive shaft 43.

The outer rotor 42B is provided radially outward of the inner rotor 42A, and rotates as the inner rotor 42A rotates. The oil pump 41 accommodates oil between the external teeth and the internal teeth by contact between a plurality of internal teeth (not shown) formed on the outer rotor 42B and a plurality of external teeth (not shown) formed on the inner rotor 42A. A plurality of working chambers (not shown) are formed.

In the pump body 42, when the power of the engine 3 is transmitted from the counter shaft 12 to the inner rotor 42A via the drive shaft 43, the inner rotor 42A and the outer rotor 42B rotate in one direction.

At this time, as the volume of the working chamber continuously increases and decreases, oil is sucked into the working chamber from a suction port (not shown), and oil pressurized by the working chamber is discharged from a discharge port (not shown).

A shaft fitting portion 12b is formed at the rear end portion 12a of the counter shaft 12, and the front end portion of the drive shaft 43 is fitted into the shaft fitting portion 12b and rotates integrally with the counter shaft 12.

The drive shaft 43 extends rearward from the counter shaft 12, and its rear end in the extending direction is connected to the inner rotor 42A. Thereby, when the counter shaft 12 rotates, the inner rotor 42A rotates integrally with the drive shaft 43. In this way, the pump body 42 and the drive shaft 43 are provided coaxially with the counter shaft 12.

The drive shaft 43 is formed to have a smaller diameter than the counter shaft 12, and extends from the rear end 12a of the counter shaft 12 through an area surrounded by the chain 39 when viewed from the axial direction of the counter shaft 12 to the inner rotor 42A. It is extending.

A rear wall 8C of the transfer case 8 is located behind the counter shaft 12. A pump accommodating portion 44 is provided on the rear wall 8C, and the pump accommodating portion 44 bulges rearward from the rear wall 8C.

The pump main body 42 is rotatably housed in a pump housing section 44 . As shown in FIGS. 2 and 6, the pump accommodating part 44 is located on the virtual straight line L, is provided in line with the bearing support part 34 in the vehicle width direction, and is connected to the bearing support part 34.

As shown in FIGS. 3 and 4, the rear wall 8C is located behind the first flat wall portion 45 and the first flat wall portion 45, and has a stepped portion 46 on the first flat wall portion 45. A second flat wall portion 47 is connected thereto. Note that FIG. 3 is a view of the transfer case 8 rotated in the horizontal direction and viewed diagonally from the rear left. Similarly, FIG. 4 is a view of the transfer case 8 rotated in the horizontal direction and viewed diagonally from the front right.

The bearing support portion 34 is provided on the second flat wall portion 47 , and the bearing support portion 35 is provided on the first flat wall portion 45 . Therefore, as shown in FIG. 3, the bearing support part 34 and the bearing support part 35 are provided at different levels on the rear wall 8C in the axial direction of the counter shaft 12. In other words, as shown in FIG. 6, the bearing support part 35 is installed to be more forward than the bearing support part 34.

As shown in FIG. 2, the pump housing section 44 is provided on the rear wall 8C so as to straddle the first flat wall section 45 and the second flat wall section 47, and as shown in FIG. It bulges out further rearward than the second flat wall portion 47 in the axial direction of the second flat wall portion 12 .

As shown in FIGS. 2 and 3, the second flat wall portion 47 includes a cylindrical first oil passage portion 48, a second oil passage portion 49, a box-shaped frame 50, and an oil passage portion 48. A supply section 51 is provided. The first oil passage section 48 bulges rearward from the second flat wall section 47 and has a lower end connected to the pump housing section 44 .

An oil passage 48a is formed inside the first oil passage part 48, and oil discharged from the working chamber of the pump body 42 and then discharged from the discharge port of the pump accommodating part 44 is stored in the oil passage 48a. Supplied. The oil supplied to the oil passage 48a is supplied to lubricated parts inside the transmission case 4.

The first oil passage section 48 extends upward from the pump accommodating section 44, and has an upper end located on the peripheral wall 8A. The first oil passage section 48 of this embodiment constitutes the oil passage section of the present invention.

The second oil passage portion 49 bulges rearward from the second flat wall portion 47 . An oil passage 49a is formed inside the second oil passage part 49, and oil flowing through the oil passage 49a is supplied to the working chamber of the pump body 42 through the suction port of the pump housing part 44.

The frame body 50 is located above the bearing support part 34 and extends rearward from the second flat wall part 47. A flange portion 50A is formed at the rear end of the frame 50, and a flange portion (not shown) of the extension case 9 (see FIG. 1) is joined to the flange portion 50A by bolts (not shown).

An operating shaft and a shift shaft of the transfer actuator 40 are housed inside the frame body 50 and the extension case 9.

The frame body 50 is installed above the bearing support part 34 so as to cross the bearing support part 34 . The first oil passage section 48 bulges out from the second flat wall section 47 to the rear beyond the frame body 50 and the bearing support section 34, and connects the frame body 50, the bearing support section 34, and the pump housing section 44. are doing.

The oil supply section 51 is located below the bearing support section 34 and bulges rearward from the second flat wall section 47 . An oil filter (not shown) is installed inside the oil supply section 51 to filter oil.

As shown in FIG. 5, when the transfer rear case 8 is viewed from the front, the oil supply section 51 has a cover 51A attached to it with bolts 58, and the oil filter is located between the oil supply section 51 and the cover 51A. is set up.

When the pump body 42 is driven, the oil stored at the bottom of the transmission case 4 is introduced into the oil supply section 51, filtered by an oil filter, and then passed through the second oil passage section 49 to the pump housing section 44. It is sucked into the working chamber of the pump body 42 through the suction port.

As shown in FIGS. 3 and 4, the second oil passage portion 49 bulges out from the second flat wall portion 47 to the rear of the pump housing portion 44 and the oil supply portion 51. An oil supply section 51 is connected thereto.

A cylindrical third oil passage portion 52 is provided on the rear wall 8C. The third oil passage portion 52 bulges rearward from the rear wall 8C, and connects the first oil passage portion 48 and the bearing support portion 34. An oil passage 52a is formed inside the third oil passage portion 52. Note that the oil passages 48a, 49a, and 52a are closed by plugs.

A part of the oil flowing through the oil passage 48a of the first oil passage part 48 is supplied to the ball bearing 14C of the bearing support part 34 through the oil passage 52a of the third oil passage part 52. Thereby, the ball bearing 14C is lubricated with oil.

The rear wall 8C is provided with ribs 53A to 53F, and the ribs 53A to 53F protrude rearward from the rear wall 8C.

The rib 53A connects the bearing support 34 and the frame 50, and the rib 53B extends from the bearing support 34 to the peripheral wall 8A. The rib 53C extends from the bearing support part 34 to the peripheral wall 8A, and the rib 53D connects the bearing support part 34 and the oil supply part 51.

The rib 53E connects the bearing support part 34 and the second oil passage part 49, and the rib 53F connects the bearing support part 34 and the first oil passage part 48. Therefore, the rigidity of the second flat wall portion 47 around the pump accommodating portion 44 is increased by the ribs 53A to 53F.

As shown in FIGS. 3 and 4, a bulge 54 is provided on the rear wall 8C. The bulging portion 54 bulges rearward from the rear wall 8C and extends in the vehicle width direction from the pump housing portion 44 and the stepped portion 46 toward the bearing support portion 35.

The pump housing part 44 is provided between the bearing support part 34 and the bearing support part 35, and is installed so as to be biased toward the bearing support part 34 side rather than the bearing support part 35 in the vehicle width direction.

As shown in FIG. 5, the upper part 54a of the bulging part 54 is located above the imaginary straight line L, and the lower part 54b of the bulging part 54 is located below the imaginary straight line L.

As shown in FIGS. 2 and 3, ribs 55A and 55B are provided on the rear wall 8C. The rib 55A extends in the vehicle width direction along the bulging portion 54 or in the vehicle width direction along the virtual straight line L, and connects the bearing support portion 35 and the pump housing portion 44.

The rib 55B is located below the rib 55A and extends in the vehicle width direction along the bulge 54. The rib 55B connects the bearing support portion 35 and the stepped portion 46.

As shown in FIGS. 2 and 3, a sensor mounting portion 56 is formed in the step portion 46 above the pump accommodating portion 44. As shown in FIGS. The sensor mounting portion 56 is formed with a sensor mounting surface 56A that is inclined diagonally downward and to the left from the first oil passage portion 48 toward the pump accommodating portion 44 .

As shown in FIG. 5, the sensor mounting portion 56 bulges out from the stepped portion 46 toward the rear output shaft 11, and as shown in FIG. It is connected.

As shown in FIGS. 5 and 6, a parking gear 25 is provided on the rear output shaft 11. A parking pole (not shown) of a parking lock mechanism (not shown) is fitted into the parking gear 25 . As a result, rotation of the rear output shaft 11 is restricted, and the stopped state of the vehicle 1 is maintained.

A rear output shaft rotation sensor 61 is attached to the sensor attachment portion 56 . Specifically, the rear output shaft rotation sensor 61 has a detection element (not shown) and a connector body (not shown). The detection element is housed in the sensor mounting portion 56, and the sensor body is attached to the sensor mounting portion 56 with bolts (not shown) so as to be in contact with the sensor mounting surface 56A.

As shown in FIG. 6, the rear output shaft 11 is provided with an exciter ring 57. The exciter ring 57 is provided with an uneven portion continuous in the circumferential direction on the outer circumference, and the rear output shaft rotation sensor 61 detects the uneven portion of the exciter ring 57 and outputs detection information to a controller (not shown). .

The controller detects the rotation speed of the rear output shaft 11 based on information output from the rear output shaft rotation sensor 61.

Next, the effects of the automatic transmission 2 of this embodiment will be explained.
According to the automatic transmission 2 of this embodiment, the transfer case 8 has a rear wall 8C located behind the counter shaft 12.

The rear wall 8C is provided with a pump accommodating portion 44 that accommodates the oil pump 41, and a cylindrical bearing support portion 34 that rotatably supports the rear output shaft 11 via a ball bearing 14C. The portion 44 is connected to the bearing support portion 34.

Thereby, the pump housing part 44 can be reinforced by the highly rigid bearing support part 34 having the highly rigid ball bearing 14C, and the rigidity of the pump housing part 44 can be increased. Therefore, vibration and deformation of the pump accommodating portion 44 due to vibrations of the automatic transmission 2 can be suppressed, and the axial center of the oil pump 41 can be prevented from swinging. Note that the axial center of the oil pump 41 is the same as the axis of the drive shaft 43.

On the other hand, the automatic transmission 2 is provided coaxially with an input shaft 10 to which power is transmitted from the engine 3, and a front end 11a is connected to a rear end 10a of the input shaft 10 so as to be relatively rotatable. A rear output shaft 11 is provided.

The automatic transmission 2 is installed parallel to the input shaft 10 and the rear output shaft 11, and the input shaft 10 and the rear output shaft 11 are provided with input gears 15A, 15B, counter gears 16A, 16B, counter drive gear 16D and It includes a counter shaft 12 connected via a counter driven gear 18, an input shaft 10, a rear output shaft 11, and a front output shaft 13 installed parallel to the counter shaft 12.

As a result, the input shaft 10, the rear output shaft 11, and the counter There is a risk that the distance between the shaft 12 and the shaft 12 will increase, and that the input shaft 10, the rear output shaft 11, and the counter shaft 12 may be deformed.

Hereinafter, the repulsive force caused by the meshing of the input gears 15A, 15B, 15C and the counter gears 16A, 16B, 16C, and the repulsive force caused by the meshing of the counter drive gear 16D and the counter driven gear 18 will be referred to as a meshing repulsive force F1. FIG. 7 shows the meshing repulsive force F1.

The automatic transmission 2 of this embodiment includes a chain 39 that is wrapped around the rear output shaft 11 and the front output shaft 13 and transmits the power of the rear output shaft 11 to the front output shaft 13. When viewed from the axial direction, the counter shaft 12 is installed between the rear output shaft 11 and the front output shaft 13, and its axis O1 is located within a region surrounded by the chain 39.

Thereby, the tension F2 of the chain 39 can bias the rear output shaft 11 and the front output shaft 13 in a direction toward each other. Therefore, it is possible to suppress the distance between the input shaft 10, the rear output shaft 11, and the counter shaft 12 from increasing, and to suppress deformation of the input shaft 10, the rear output shaft 11, and the counter shaft 12. .

Therefore, it is possible to more effectively prevent the axial center of the oil pump 41 connected to the counter shaft 12 from swinging. As a result, the suction efficiency and durability of the oil pump 41 can be prevented from deteriorating.

Further, the meshing between the input gears 15A, 15B and the counter gears 16A, 16B and the meshing between the counter drive gear 16D and the counter driven gear 18 can be maintained normally, and the NV performance of the automatic transmission 2 can be prevented from deteriorating.

Further, in the automatic transmission 2 of this embodiment, when viewed from the axial direction of the counter shaft 12, the rear output shaft 11, the counter shaft 12, and the front output shaft 13 are aligned with the axis O1 of the rear output shaft 11. The axial center O2 of the counter shaft 12 and the axial center O3 of the front output shaft 13 are arranged so as to be aligned on a virtual straight line L.

Thereby, the tension F2 of the chain 39 can be applied most effectively so that the rear output shaft 11 and the front output shaft 13 can be biased toward each other. Therefore, it is possible to more effectively suppress the distance between the input shaft 10, the rear output shaft 11, and the counter shaft 12 from increasing, and the input shaft 10, the rear output shaft 11, and the counter shaft 12 are deformed. This can be suppressed more effectively.

As a result, it is possible to more effectively prevent the axial center of the oil pump 41 connected to the counter shaft 12 from swinging due to vibrations of the automatic transmission 2, etc., and to further prevent deterioration of the suction efficiency and durability of the oil pump 41. Can be effectively prevented.

Further, according to the automatic transmission 2 of the present embodiment, the oil pump 41 extends rearward from the counter shaft 12 coaxially with the pump body 42 housed in the pump accommodating portion 44 and the counter shaft 12 . The drive shaft 43 has a drive shaft 43 connected to the chain 39, and the drive shaft 43 passes through an area surrounded by the chain 39.

Thereby, the drive shaft 43 can be installed in the transfer rear case 8 by utilizing the dead space inside the chain 39. Therefore, the space for installing the drive shaft 43 can be reduced, and the transmission case 4 can be made smaller. As a result, the automatic transmission 2 can be made smaller.

Further, according to the automatic transmission 2 of the present embodiment, the rear wall 8C is located behind the first flat wall portion 45 and the first flat wall portion 45, and the rear wall 8C is connected to the first flat wall portion 45. A second flat wall portion 47 is connected to the second flat wall portion 47 via a step portion 46.

The bearing support portion 34 is provided on the second flat wall portion 47 , and the pump housing portion 44 straddles the first flat wall portion 45 and the second flat wall portion 47 and extends in the axial direction of the counter shaft 12 . It bulges out further rearward than the second flat wall portion 47 . In other words, the pump accommodating portion 44 is formed to extend from both the first flat wall portion 45 and the second flat wall portion 47 to the rear side of the second flat wall portion 45 in the axial direction of the counter shaft 12. ing.

Thereby, the rear wall 8C of the transfer case 8 can be formed into an uneven shape by the first flat wall part 45, the step part 46, and the second flat wall part 47, and when the rear wall 8C is flat, In comparison, the surface rigidity of the rear wall 8C can be improved.

Furthermore, by providing the pump accommodating portion 44 in the step portion 46 having high rigidity, the rigidity of the pump accommodating portion 44 can be further increased.

Therefore, it is possible to more effectively suppress vibration and deformation of the pump accommodating portion 44 due to vibrations of the automatic transmission 2, etc., and to more effectively suppress vibrations of the axial center of the oil pump 41 connected to the counter shaft 12. can be prevented. As a result, it is possible to more effectively prevent the suction efficiency and durability of the oil pump 41 from deteriorating.

Further, according to the automatic transmission 2 of the present embodiment, the second flat wall portion 47 bulges rearward from the second flat wall portion 47, and the lower end portion is connected to the first pump housing portion 44. It has an oil passage section 48 and a box-shaped frame body 50 located above the bearing support section 34 and extending rearward from the second flat wall section 47 .

The pump accommodating portion 44 is provided on the virtual straight line L, and the first oil passage portion 48 extends upward from the pump accommodating portion 44 .

In addition, the frame 50 is installed above the bearing support 34 so as to cross the bearing support 34, and the first oil passage 48 is connected from the second flat wall 47 to the frame 50. It bulges out further back than the bearing support part 34, and connects the frame body 50 and the bearing support part 34.

As a result, the second flat wall portion 47 of the rear wall 8C of the transfer case 8 can be reinforced by the first oil passage portion 48 and the frame body 50, which have high rigidity, respectively, and the rigidity of the second flat wall portion 47 can be increased. can be made even higher.

In addition, the first oil passage section 48 connected to the pump accommodating section 44 can be reinforced by the highly rigid bearing support section 34 and the frame 50, making it possible to further increase the rigidity of the first oil passage section 48. . Therefore, the rigidity of the pump accommodating portion 44 can be further increased.

Therefore, it is possible to more effectively suppress vibration and deformation of the pump accommodating portion 44 due to vibrations of the automatic transmission 2, etc., and it is possible to more effectively suppress vibration of the axial center of the oil pump 41 connected to the counter shaft 12. can be prevented. As a result, it is possible to more effectively prevent the suction efficiency and durability of the oil pump 41 from deteriorating.

Further, according to the automatic transmission 2 of the present embodiment, the second flat wall portion 47 includes a second oil passage portion 49 that bulges rearward from the second flat wall portion 47 and a portion of the bearing support portion 34 . It has an oil supply section 51 located below, bulging rearward from the second flat wall section 47, and supplying oil to the second oil passage section 49.

In addition, the second oil passage section 49 bulges out from the second flat wall section 47 to the rear of the pump housing section 44 and the oil supply section 51, and connects the pump housing section 44 and the oil supply section 51. ing.

Thereby, the pump accommodating part 44 can be reinforced by the first oil passage part 48 and the second oil passage part 49, which have high rigidity, and the rigidity of the pump accommodating part 44 can be further increased.

In addition, since the pump accommodating part 44 and the oil supply part 51 are connected by the second oil passage part 49, the rigidity of the second oil passage part 49 can be further increased by the oil supply part 51. The second oil passage section 49, which has even higher rigidity, can further increase the rigidity of the pump accommodating section 44.

Therefore, it is possible to more effectively suppress vibration and deformation of the pump accommodating portion 44 due to vibrations of the automatic transmission 2, etc., and to more effectively suppress vibrations of the axial center of the oil pump 41 connected to the counter shaft 12. can be prevented. As a result, it is possible to more effectively prevent the suction efficiency and durability of the oil pump 41 from deteriorating.

Further, according to the automatic transmission 2 of this embodiment, the first flat wall portion 45 of the rear wall 8C is connected to the bearing support portion 35 that rotatably connects the front output shaft 13 via the ball bearing 14F, and the rear It has a bulging portion 54 that bulges rearward from the wall 8C.

The pump housing portion 44 is provided between the bearing support portion 34 and the bearing support portion 35, and the bulging portion 54 extends from the pump housing portion 44 and the stepped portion 46 toward the bearing support portion 35.

In addition, the upper part 54a of the bulging part 54 is located above the imaginary straight line L, and the lower part 54b of the bulging part 54 is located below the imaginary straight line L.

Thereby, the rigidity of the first flat wall portion 45 can be increased by the bulge portion 54. Therefore, when the counter shaft 12 attempts to move away from the input shaft 10 and the rear output shaft 11 due to the meshing repulsive force F1, the load of the counter shaft 12 can be received by the highly rigid bulge 54.

In addition to this, the load applied from the counter shaft 12 to the bulge 54 can be distributed from the bulge 54 to the bearing support portion 35.

Therefore, it is possible to more effectively suppress the distance between the input shaft 10, the rear output shaft 11, and the counter shaft 12 from increasing, and to reduce the deflection of the input shaft 10, the rear output shaft 11, and the counter shaft 12. This can be more effectively suppressed.

As a result, the axial center of the oil pump 41 connected to the counter shaft 12 can be more effectively prevented from swinging, and the suction efficiency and durability of the oil pump 41 can be more effectively prevented from deteriorating.

Further, according to the automatic transmission 2 of this embodiment, ribs 55A and 55B are provided on the rear wall 8C. The rib 55A extends in the vehicle width direction along the bulging portion 54 and connects the bearing support portion 35 and the pump housing portion 44.

The rib 55B is located below the rib 55B and extends in the vehicle width direction along the bulge 54. In addition, the rib 55B connects the bearing support portion 35 and the stepped portion 46.

Thereby, the rigidity of the first flat wall portion 45 can be increased by the bulge 54, and the load applied from the counter shaft 12 to the bulge 54 can be dispersed by the ribs 55A and 55B.

Therefore, it is possible to more effectively suppress the distance between the input shaft 10, the rear output shaft 11, and the counter shaft 12 from increasing, and to reduce the deflection of the input shaft 10, the rear output shaft 11, and the counter shaft 12. This can be more effectively suppressed.

Further, according to the automatic transmission 2 of this embodiment, the sensor mounting portion 56 is formed in the stepped portion 46 above the pump accommodating portion 44, and the sensor mounting portion 56 is connected to the rear output shaft from the stepped portion 46. 11, and connects the first oil passage section 48 and the pump housing section 44.

Thereby, the rigidity of the pump accommodating part 44 can be further increased by the sensor attachment part 56, and vibration and deformation of the pump accommodating part 44 can be more effectively prevented.

Although embodiments of the invention have been disclosed, it will be apparent that modifications may be made by one 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.

1...Vehicle, 2...Automatic transmission (vehicle transmission), 3...Engine (drive source), 4...Transmission case, 8C...Rear wall (vertical wall), 10 ...Input shaft (first rotating shaft), 10a... Rear end (end in the axial direction of the first rotating shaft), 11... Rear output shaft (second rotating shaft), 11a... Front end (end in the axial direction of the second rotating shaft), 12... Counter shaft (third rotating shaft), 13... Front output shaft (fourth rotating shaft), 14C , 14F...ball bearing (bearing), 15A...first input gear (gear pair, first gear), 15B...second input gear (gear pair), 15C...third input gear (gear pair), 16A...first counter gear (gear pair), 16B...second counter gear (gear pair), 16C...third counter gear, 16D... Counter drive gear (gear pair), 17...clutch gear (gear pair), 18...counter driven gear (gear pair), 39...chain, 41...oil pump, 42...pump body, 43... Drive shaft, 44... Pump accommodating part, 45... First flat wall part, 46... Step part, 47... Second flat wall part, 48... First oil passage section (oil passage section), 49...second oil passage section, 50...frame body, 51...oil supply section, 54...bulging section, 54a...upper part ( upper part of the bulging part), 54b...lower part (lower part of the bulging part), L...virtual straight line, O1...axis center (axis center of the third rotating shaft), O2...axis center (Axis center of the second rotating shaft), O3...Axis center (Axis center of the fourth rotating shaft)

Claims (6)

a first rotating shaft to which power is transmitted from a drive source; and a first rotating shaft provided coaxially with the first rotating shaft;
a second rotating shaft whose axial end is relatively rotatably connected to the axial end of the first rotating shaft;
a third rotating shaft installed parallel to the first rotating shaft and the second rotating shaft and connected to the first rotating shaft and the second rotating shaft via a plurality of gear pairs;
a fourth rotation axis installed parallel to the first rotation axis, the second rotation axis, and the third rotation axis;
a chain that is wrapped around the second rotating shaft and the fourth rotating shaft and transmits the power of the second rotating shaft to the fourth rotating shaft;
an oil pump driven by the third rotating shaft;
a transmission case that accommodates the first rotating shaft, the second rotating shaft, the third rotating shaft, and the fourth rotating shaft,
The transmission case has a vertical wall located behind the third rotating shaft,
The vertical wall includes a first flat wall portion and a second flat wall portion located rearward of the first flat wall portion and connected to the first flat wall portion via a step. has
A cylindrical bearing support part that rotatably supports the second rotating shaft via a bearing is provided on the second flat wall part ,
A pump accommodating portion for accommodating the oil pump is provided in the first flat wall portion and the second flat wall portion ,
The pump accommodating portion straddles the first flat wall portion and the second flat wall portion and bulges rearward than the second flat wall portion in the axial direction of the third rotating shaft,
When viewed from the axial direction of the third rotating shaft, the third rotating shaft is installed between the second rotating shaft and the fourth rotating shaft, and the axial center thereof is surrounded by the chain. It is located within the area covered by
The vehicle transmission, wherein the pump housing section is connected to the bearing support section. When viewed from the axial direction of the third rotating shaft, the second rotating shaft, the third rotating shaft, and the fourth rotating shaft are aligned with the axis of the second rotating shaft and the third rotating shaft. 2. The vehicle transmission according to claim 1, wherein the axial center of the rotating shaft and the axial center of the fourth rotating shaft are arranged so as to be aligned on a virtual straight line. The oil pump includes a pump body housed in the pump housing portion, and a drive shaft that extends rearward from the third rotation shaft coaxially with the third rotation shaft and is connected to the pump body. death,
3. The vehicle transmission according to claim 2, wherein the drive shaft passes through an area surrounded by the chain. The second flat wall portion bulges rearward from the second flat wall portion, and is located above an oil passage portion whose lower end portion is connected to the pump housing portion, and the bearing support portion, and is located above the bearing support portion. a box-shaped frame body extending rearward from the flat wall portion of 2;
The pump housing section is provided on the virtual straight line,
The oil passage portion extends upward from the pump housing portion,
The frame body is installed above the bearing support part so as to cross the bearing support part,
2. The oil passage portion bulges out from the second flat wall portion to the rear of the frame body and the bearing support portion, and connects the frame body and the bearing support portion. Or the vehicle transmission according to claim 3. When the oil passage portion is a first oil passage portion, the second flat wall portion includes a second oil passage portion that bulges rearward from the second flat wall portion, and the bearing support portion. an oil supply part located below the second flat wall part and bulging rearward from the second flat wall part to supply oil to the second oil passage part;
The second oil passage portion bulges out from the second flat wall portion to the rear of the pump accommodating portion and the oil supply portion, and connects the pump accommodating portion and the oil supply portion. The vehicle transmission according to claim 4. When the bearing support section is a first bearing support section, the vertical wall includes a second bearing support section that rotatably connects the fourth rotating shaft via a bearing, and a second bearing support section that connects the fourth rotation shaft rearwardly from the vertical wall. It has a bulging part that bulges out,
The pump housing section is provided between the first bearing support section and the second bearing support section,
The bulging portion extends from the pump accommodating portion and the stepped portion toward the second bearing support portion,
An upper part of the bulging part is located above the imaginary straight line, and a lower part of the bulging part is located below the imaginary straight line . The vehicle transmission according to any one of the items .

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