WO2006095784A1 - 車輌用自動変速機 - Google Patents
車輌用自動変速機 Download PDFInfo
- Publication number
- WO2006095784A1 WO2006095784A1 PCT/JP2006/304497 JP2006304497W WO2006095784A1 WO 2006095784 A1 WO2006095784 A1 WO 2006095784A1 JP 2006304497 W JP2006304497 W JP 2006304497W WO 2006095784 A1 WO2006095784 A1 WO 2006095784A1
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- WIPO (PCT)
- Prior art keywords
- clutch
- transmission
- planetary gear
- input
- rotation
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
- F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
- F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
Definitions
- the present invention relates to an automatic transmission mounted on a vehicle or the like, and more specifically, the first and second input transmission clutches and the first and second reduction transmission clutches,
- the present invention relates to an arrangement structure of an automatic transmission that enables multistage speed change by allowing input rotation and reduced speed rotation to be transmitted to second and third rotation elements.
- 1st and 2nd reduction transmission clutches (C2, C1) that enable transmission of reduced rotation via the gear (C4, C3) and reduction planetary gear (G1), and the first that fixes rotation to the case (1)
- the first rotation element can transmit the input rotation by the first input transmission clutch (C4) and the deceleration rotation by the first deceleration transmission clutch (C2) to the first rotation element (S2) of the planetary gear set (G23).
- a member that connects the first input transmission clutch (C4) and the first rotating element (S2) in the automatic transmission ie, the output side of the first input transmission clutch
- the clutch and the brake are arranged so that the member is arranged on the outer peripheral side from the path for inputting the input rotation to the third rotating element (PC2 and PC3) via the second input transmission clutch (C3).
- a member that may have a higher rotational speed than the input rotation is disposed on the outer peripheral side of the member that does not have a higher rotational speed than the input rotation, and a member that requires high rigidity is disposed.
- an object of the present invention is to provide an automatic transmission for a vehicle that can reduce the inertia and improve the controllability while enabling light weight. .
- the present invention includes a rotation fixing element (S1) whose rotation is fixed to the case (4), and an input rotation element (the input rotation of the input shaft (12)).
- CR1 and the speed reduction planetary gear (DP) having the speed reduction rotation element (R1) that outputs the speed reduction rotation with the input speed reduced, and the first, second, third, A planetary gear set (PU) having four rotating elements (S 2, S3, CR2, R3) and the first rotating element (S2)
- a first input transmission clutch (C 4) capable of transmitting the input rotation
- a second input transmission clutch (C 2) capable of transmitting the input rotation to the third rotation element (CR 2);
- the first deceleration transmission clutch (C 3) capable of transmitting the reduced rotation through the reduction planetary gear (DP) to the rotation element (S2), and the reduction planetary gear (DP) to the second rotation element (S3).
- a second deceleration transmission clutch (C 1) capable of transmitting the decelerated rotation after passing through, a first brake (B-1) capable of locking the rotation of the first rotation element (S2) with respect to the case, A second brake (B-2) capable of locking the rotation of the third rotating element (CR2) with respect to the case (4), and the fourth rotating element (R3) force output rotation.
- vehicle automatic transmission (1) that can output,
- the output transmission member (103) of the second input transmission clutch (C 2) is the output transmission member (101, 102) of the first and second deceleration transmission clutches (C-3, C-1). Is connected to the third rotating element (CR2) through the outer peripheral side of
- the side transmission member (101) is connected to the first rotating element (S2) and rotates integrally with the first transmission element (104, FIG. 8) of the first input transmission clutch (C4). 13 in FIG. 18, 101 in FIGS. 15 and 16, and the output transmission member (101) of the first deceleration transmission clutch (C-3) is the output of the second deceleration transmission clutch (C 1). It is arranged on the inner peripheral side with respect to the side transmission member (102).
- the output-side transmission member force of the first input transmission clutch that is higher in rotation than the output-side transmission member of the second input transmission clutch.
- the inner circumference of the output-side transmission member of the second input transmission clutch The inner diameter of the output transmission member of the second input transmission clutch is smaller than the diameter of the output transmission member of the second input transmission clutch.
- inertia inertial force
- controllability can be improved as an automatic transmission for a vehicle.
- the present invention (see, for example, FIG. 1, FIGS. 5 to 7, FIGS. 11 to 14, and FIG. 19), a rotation fixing element (S1) whose rotation is fixed to the case (4), and an input shaft (12)
- the input rotation at which the input rotation is input The speed reduction planetary gear (DP) having a rotation element (CR1) and a speed reduction rotation element (R1) that outputs a reduction speed reduction of the input speed, and the first, second, third, which are arranged in a rotational speed relationship due to the meshing relationship
- a planetary gear set (PU) having a fourth rotating element (S2, S3, CR2, R3), a first input transmission clutch (C4) capable of transmitting the input rotation to the first rotating element (S2), and A second input transmission clutch (C 2) capable of transmitting the input rotation to the third rotation element (CR2), and a decelerated rotation through the reduction planetary gear (DP) to the first rotation element (S2).
- the first and second reduction transmission clutches (C-3, C-1) are disposed on the reduction planetary gear (DP) side with respect to the planetary gear set (PU), and the first and second reduction gears Connecting the output side transmission members (101, 102) of the transmission clutch (C-3, C-1) to the first rotating element (S2) and the second rotating element (S3), respectively;
- the first input transmission clutch (C-4) is disposed on the opposite side of the planetary gear set (PU) from the reduction planetary gear (DP) in the axial direction, and the first input transmission clutch (C 4) connecting the output side transmission member (104) to the first rotating element (S2), and connecting the second input transmission clutch (C-2) to the planetary gear set (PU).
- (DP) side and the output transmission member (103) of the second input transmission clutch (C-2) is connected to the first and second reduction transmission clutches (C-3, C-1).
- the output-side transmission members (101, 102) of the first and second transmission elements (101, 102) are connected to the third rotating element (CR2) through the outer peripheral side.
- the output-side transmission member of the first input transmission clutch which rotates at a higher speed than the output-side transmission member of the second input transmission clutch, is on the inner peripheral side, so the output side of the first input transmission clutch
- the diameter of the transmission member can be made smaller than the diameter of the output-side transmission member of the second input transmission clutch, and a lighter weight can be achieved than when it is on the outer peripheral side. Also when outside Inertia (inertial force) can be reduced compared to the above, so that it is possible to improve control performance as an automatic transmission for vehicles.
- the friction plate of the first input transmission clutch is disposed relatively on the outer peripheral side as compared with the hydraulic servo of the first input transmission clutch disposed between the planetary gear set and the reduction planetary gear. Since the area of the friction plate can be increased, a torque capacity that can be transmitted can be ensured, and the number of friction plates can be reduced.
- the distance between the first and second reduction transmission clutches and the planetary gear set can be shortened, and the transmission on the output side of the first and second reduction transmission clutches that require strength to transmit high torque.
- the member can be shortened. As a result, the weight can be reduced, and the controllability can be improved as an automatic transmission for a vehicle.
- the present invention includes an input side transmission member (52) of the first input transmission clutch (C-4),
- the planetary gear set (PU) is coupled to the input shaft (12, 13) passing through the inner peripheral side of the planetary gear set (PU), and a part of the input side transmission member (52) of the first input transmission clutch (C4) is It is configured as a clutch drum (52) of the hydraulic servo (50) of the first input transmission clutch (C4).
- the clutch drum of the hydraulic servo also serves as the power transmission member having the input axial force as compared with the case where a part of the output side transmission member of the first input transmission clutch is configured as a clutch drum of the hydraulic servo. Therefore, it is possible to make it compact in the axial direction.
- the present invention (see, for example, FIG. 8, FIG. 15, FIG. 16, FIG. 18), the rotation fixing element (S1) whose rotation is fixed to the case (4), and the input rotation of the input shaft (12)
- 2nd, 3rd A planetary gear set (PU) having a fourth rotation element (S2, S3, CR2, R3), and a first input transmission clutch (C4) capable of transmitting the input rotation to the first rotation element (S2).
- the second input transmission clutch (C 2) capable of transmitting the input rotation to the third rotation element (CR2), and the reduced rotation through the reduction planetary gear (DP) to the first rotation element (S2).
- a first reduction transmission clutch (C 3) that can be transmitted, and a second reduction transmission clutch (C-1) that can transmit the reduction rotation through the reduction planetary gear (DP) to the second rotation element (S3).
- the first brake (B 1) that can lock the rotation of the first rotating element (S2) with respect to the case, and the rotation of the third rotating element (CR2) to the case (4).
- a vehicle-mounted automatic transmission (1) including a second brake (B-2) that can be locked to the vehicle and capable of outputting output rotation from the fourth rotating element (R3);
- the first and second reduction transmission clutches (C-3, C-1) are disposed on the reduction planetary gear (DP) side with respect to the planetary gear set (PU), and the first and second reduction gears Connecting the output side transmission members (101, 102) of the transmission clutches (C-3, C-1) to the first rotating element (S2) and the second rotating element (S3), respectively;
- the first input transmission clutch (C-4) is disposed on the speed reduction planetary gear (DP) side with respect to the planetary gear set (PU), and the output of the first input transmission clutch (C-4).
- Side transmission members 13 in FIGS. 8 and 18, 101 in FIGS. 15 and 16) are connected to the first rotating element (S2),
- the second input transmission clutch (C-2) is disposed on the reduction planetary gear (DP) side with respect to the planetary gear set (PU), and the output of the second input transmission clutch (C-2).
- Side transmission member (103) through the outer peripheral side of the output side transmission members (101, 102) of the first and second deceleration transmission clutches (C-3, C-1). ).
- the output-side transmission member of the first input transmission clutch which rotates at a higher speed than the output-side transmission member of the second input transmission clutch, is on the inner peripheral side, so the output side of the first input transmission clutch
- the diameter of the transmission member can be made smaller than the diameter of the output-side transmission member of the second input transmission clutch, and a lighter weight can be achieved than when it is on the outer peripheral side.
- inertia inertial force
- controllability can be improved.
- the input-side transmission member (52) of the first input transmission clutch (C 4) is connected to the input rotation element ( It is directly connected to CR1) and is configured as a part of the hydraulic servo (50) of the first input transmission clutch (C4) together with a part of the input rotation element (CR1).
- the compact size can be lightweight.
- the present invention (see, for example, FIGS. 1, 11, 16 to 19) is connected to the side wall (3a) of the case (4) and fixes the rotation fixing element (S1). (3b), and the input side transmission member (32) of the second input transmission clutch (C2) is coupled to the input rotation element (CR1), and the second input transmission clutch (C2 A part of the input side transmission member (32) of 2) is configured as a clutch drum (32) of the hydraulic servo (30) of the second input transmission clutch (C 2), and the hydraulic servo (30) It is arranged on the boss part (3b) between the reduction planetary gear (DP) and the side wall (3a) in the axial direction.
- the input side transmission member (111) of the second deceleration transmission clutch (C 1) is connected to the deceleration rotation element ( R1)
- the output transmission member (102) of the second reduction transmission clutch (C1) is connected to the second rotation element (S3)
- the second reduction transmission clutch (C1) A part of the output transmission member (102) of —1) is configured as a clutch drum (22) of the hydraulic servo (20) of the second deceleration transmission clutch (C—1), and the hydraulic servo (20)
- the hydraulic oil provided in the box portion connected to the side wall of the case can be supplied to the hydraulic servo of the second reduction transmission clutch by the hydraulic oil.
- the hydraulic servo of the second deceleration transmission clutch is arranged on the input shaft away from the boss portion force and hydraulic oil is supplied via the oil passage in the input shaft,
- the length of the oil passage can be shortened by not interposing the oil passage, and as a vehicle automatic transmission, controllability can be improved.
- the present invention includes a counter gear (15) connected to the fourth rotating element (R3) of the planetary gear set (PU),
- the counter gear (15) is disposed on the opposite side of the planetary gear set (PU) from the reduction planetary gear (DP) in the axial direction,
- the second brake (B-2) is a multi-plate brake composed of a plurality of friction plates (71), and the multi-plate brake is disposed on the outer peripheral side of the planetary gear set (PU).
- the second brake engagement force transmission member is shared with the output transmission member of the second input transmission clutch.
- a multi-plate brake can be arranged, and the brake can be multi-plate while maintaining a compact size.
- the present invention (see, for example, Figs. 5 to 8 and Figs. 12 to 15) is connected to the fourth rotating element (R3) and is connected to the shaft of the planetary gear set (PU) and the reduction planetary gear (DP). With counter gear (15) arranged between the directions,
- the input rotation element (112) of the second input transmission clutch (C2) passes through the outer peripheral side of the first and second deceleration transmission clutches (C-3, C-1) and the input rotation element (CR1) and the output-side transmission member (103) of the second input transmission clutch (C-2).
- a part is configured as a clutch drum (32) of a hydraulic servo (30) of the second input transmission clutch (C 2), and the hydraulic servo (30) is connected to the reduction planetary gear (DP) and the counter gear (15). ) And the support part (120a) between the axial directions.
- the present invention is also connected to the side wall (3a) of the case (4) and fixes the rotation fixing element (S1) (see, for example, Figs. 7, 8, 14, and 15).
- a boss portion (3b), and an input side transmission member (42) of the first reduction transmission clutch (C3) is coupled to the reduction rotation element (R1), and the first reduction transmission clutch
- a part of the input side transmission member (42) of (C-3) is configured as a clutch drum (42) of the hydraulic servo (40) of the first deceleration transmission clutch (C 3), and the hydraulic servo (40 ) Is disposed on the boss portion (3b) between the reduction planetary gear (DP) and the side wall (3a) in the axial direction,
- the input side transmission member (22) of the second deceleration transmission clutch (C1) is connected to the input side transmission member (42) of the first deceleration transmission clutch (C3) and the second deceleration transmission clutch (C1).
- a part of the input side transmission member (22) of the transmission clutch (C-1) is configured as a clutch drum (22) of the hydraulic servo (20) of the second deceleration transmission clutch (C1), and the hydraulic servo (20) is arranged on the support portion (120a) between the reduction planetary gear (DP) and the hydraulic servo (30) of the second input transmission clutch (C2).
- the output-side transmission member (102) of the second deceleration transmission clutch (C-1) is connected to the second rotation element (S3).
- a part of the output side transmission member (102) of the second deceleration transmission clutch (C1) is used as a clutch drum (22) of the hydraulic servo (20) of the second deceleration transmission clutch (C1).
- the hydraulic servo (20) is supported between the reduction planetary gear (DP) and the hydraulic servo (30) of the second input transmission clutch (C-2) in the axial direction.
- An output side transmission member (101) of the first deceleration transmission clutch (C3) is coupled to the first rotation element (S2), and an output side of the first deceleration transmission clutch (C-3)
- a part of the transmission member (101) is configured as a clutch drum (42) of the hydraulic servo (40) of the first deceleration transmission clutch (C-3), and the hydraulic servo (40) is configured as the reduction planetary gear (DP).
- the hydraulic servo of the first reduction transmission clutch is arranged between the planetary gear set and the reduction planetary gear in the axial direction. For example, this is compared with the case where the first reduction transmission clutch is arranged on the opposite side of the planetary gear set with respect to the reduction planetary gear.
- the distance between the first reduction transmission clutch and the planetary gear set can be shortened, and the output transmission member of the first reduction transmission clutch, which requires strength to transmit high torque, is shortened. Can do. As a result, it is possible to reduce the weight and improve the controllability of the vehicle automatic transmission.
- the present invention (see, for example, FIGS. 1 to 19) is arranged in parallel with the input shaft (12) and via a counter gear (15) connected to the fourth rotating element (R3). Connected to the second shaft (81), The output rotation from the fourth rotating element (R3) is transmitted to the second shaft (81) via the counter gear (15).
- the vehicle automatic transmission can be suitably used for an FF type vehicle.
- the counter gear (15) is disposed between the planetary gear set (PU) and the reduction planetary gear (DP) in the axial direction. At the same time, it is supported by a support portion (120a) connected to a wall (120) extending from the case (4).
- the automatic transmission can be made compact.
- the counter gear (15) is disposed on the opposite side of the planetary gear set (PU) from the reduction planetary gear (DP) in the axial direction. And supported by a support portion (120a) connected to a wall (120) extending from the case (4)).
- the distance between the speed reduction planetary gear and the planetary gear set can be shortened, and in particular, the output side members of the first and second speed reduction transmission clutches that need strength to transmit high torque can be shortened. Can do. As a result, light weight can be achieved, and controllability can be improved as a vehicle automatic transmission.
- the input rotation element (CR1) is connected to the input shaft (CR) on the planetary gear set (PU) side with respect to the deceleration planetary gear (DP). 12) and an input side transmission member of the second input transmission clutch (C 2) on the opposite side of the planetary gear set (PU) in the axial direction with respect to the reduction planetary gear (DP). (32 or 112).
- the locking force transmission member (116, 104) of the first brake (B-1) is used as the speed reduction planetary in the planetary gear set (PU). It is connected to the first rotating element (S2) on the opposite side to the re-gear (DP) in the axial direction.
- the locking force transmitting member of the first brake and the first rotating element can be connected without complicating the members, and the vehicle automatic transmission can be made compact.
- the rotation fixing element of the reduction planetary gear (DP) is a first sun gear (S1) force
- the input rotation element of the reduction planetary gear includes a first pinion gear (P1) meshed with the first sun gear (S1) and a second pinion gear meshed with the first pinion gear (P1). (P2) and a first carrier (CR1) that rotatably supports the input shaft (12) and is always connected to the input shaft (12),
- the reduction rotation element of the reduction planetary gear (DP) comprises a first ring gear (R1) that meshes with the second pinion gear (P2) and outputs the reduction rotation.
- the planetary gear set (PU) includes a second sun gear (S2), a third sun gear (S3), and the third sun gear (S3 ) Meshed with the third pinion gear (P3) meshed with the second sun gear (S2) and meshed with the third pinion gear (P3), and the third pinion gear (P4) meshed with the third pinion gear (P3).
- a second carrier (CR2) rotatably supporting the second pinion gear (P4)
- a second ring gear Rabyo type planetary gear set having R3
- the first rotating element comprises the second sun gear (S2),
- the second rotating element comprises the third sun gear (S3),
- the third rotating element comprises the second carrier (CR2),
- the fourth rotating element includes the second ring gear (R3).
- each rotating element of the planetary gear set and the output side portion of each clutch or brake Although the members can be connected to each other without complication of the members, the high rotational speed of each rotating element can be prevented and a good gear ratio can be obtained.
- the present invention engages the second deceleration transmission clutch (C 1) and engages the second brake (B-2). By engaging the second deceleration transmission clutch (C 1) and engaging the first brake (B-1), the forward second speed is achieved.
- the rotational speed relationship is the combined relationship of the first, second, third, and fourth rotational elements (S2, S3, CR3, R3).
- the rotation speed of each of the first, second, third and fourth rotation elements (S2, S3, CR3, R3) of the planetary gear set (PU) is shown on the vertical axis.
- the first rotating element (S2) is positioned at the lateral end, and the third rotating element (CR2)
- FIG. 1 is a cross-sectional view showing an automatic transmission 1 according to a first embodiment.
- FIG. 2 is a skeleton diagram showing an automatic transmission 1.
- FIG. 3 is an operation table of the automatic transmission 1.
- FIG. 4 is a speed diagram of the automatic transmission 1.
- FIG. 5 is a cross-sectional view showing an automatic transmission 1 according to a second embodiment.
- FIG. 6 is a cross-sectional view showing an automatic transmission 1 according to a third embodiment.
- FIG. 7 is an enlarged sectional view showing an automatic transmission 1 according to a fourth embodiment.
- FIG. 8 is a cross-sectional view showing an automatic transmission 1 according to a fifth embodiment.
- FIG. 9 is a skeleton diagram showing an automatic transmission 1 according to a fifth embodiment.
- FIG. 10 is an operation table of the automatic transmission 1 according to the fifth embodiment.
- FIG. 11 is a sectional view showing an automatic transmission 1 according to a sixth embodiment.
- FIG. 12 is a sectional view showing an automatic transmission 1 according to a seventh embodiment.
- FIG. 13 is a cross-sectional view showing an automatic transmission 1 according to an eighth embodiment.
- FIG. 14 is a sectional view showing an automatic transmission 1 according to a ninth embodiment.
- FIG. 15 is a sectional view showing an automatic transmission 1 according to a tenth embodiment.
- FIG. 16 is a sectional view showing an automatic transmission 1 according to an eleventh embodiment.
- FIG. 17 is a sectional view showing an automatic transmission 1 according to a twelfth embodiment.
- FIG. 18 is a sectional view showing an automatic transmission 1 according to a thirteenth embodiment.
- FIG. 19 is a sectional view showing an automatic transmission 1 according to a fourteenth embodiment.
- FIGS. 1 is a cross-sectional view showing the automatic transmission 1 according to the first embodiment
- FIG. 2 is a skeleton diagram showing the automatic transmission 1
- FIG. 3 is an operation table of the automatic transmission 1
- FIG. 4 is an automatic transmission.
- 1 is a velocity diagram of 1.
- the input shaft force also has a member on the input shaft side (that is, the upstream side of the transmission path), especially the friction plate as a boundary for one clutch,
- the member on the counter gear side (that is, the downstream side of the transmission path) is called the “output-side transmission member”.
- the automatic transmission 1 has a case 4 configured by connecting a transmission case 3 and a housing case containing a torque converter 7 and the like.
- a speed change mechanism 2 As shown in FIG. 2, a speed change mechanism 2, a countershaft portion 80, and a differential portion 90 are arranged.
- the speed change mechanism 2 is an axis centering on the input shaft 12 (of the speed change mechanism) and the intermediate shaft 13 that are coaxial with the input shaft 11 of the automatic transmission 1 connected to the output shaft of an engine (not shown), for example.
- the force countershaft 81 of the countershaft portion 80 is disposed on an axis parallel to the input shaft 12 and the intermediate shaft 13, and the differential portion 90 is connected to the countershaft 81.
- the left and right axles 931 and 93r are arranged on parallel axes.
- the input shaft 12 and the intermediate shaft 13, the counter shaft 81, and the left and right axles 931 and 93r are in a letter-like positional relationship when viewed from the side.
- the torque converter 7 includes a pump impeller 7a connected to the input shaft 11 of the automatic transmission 1, and a pump to which rotation of the pump impeller 7a is transmitted via a working fluid.
- the turbine runner 7b is connected to the input shaft 12 of the transmission mechanism 2 arranged coaxially with the input shaft 11.
- the torque converter 7 is provided with a lockup clutch 10, and when the lockup clutch 10 is engaged by hydraulic control of a hydraulic control device (not shown), the input shaft 11 of the automatic transmission 1 is engaged. Is transmitted directly to the input shaft 12 of the speed change mechanism 2.
- the speed change mechanism 2 includes a planetary gear (reduction planetary gear) DP and a planetary gear unit (planetary gear set) PU on the input shaft 12 (and an intermediate shaft 13 described later in detail).
- the planetary gear DP includes a sun gear (rotation fixed element, first sun gear) Sl, a carrier (input rotation element, first carrier) CR1, and a ring gear (deceleration rotation element, first ring gear) R1.
- the carrier CR1 has a pion (first pion gear) P1 that mates with the sun gear S1 and a pion (second pion gear) P2 that mates with the ring gear R1.
- Ru, V a so-called double beon planetary gear.
- the planetary gear unit PU has four rotation elements: a sun gear S2 (first rotation element, second sun gear), a sun gear S3 (second rotation element, third sun gear), a carrier CR2 (CR3) ( A third rotation element, a second carrier), and a ring gear R3 (R2) (fourth rotation element, a second ring gear), and a long pinion (a second rotation gear) that meshes with the sun gear S2 and the ring gear R3.
- 4 pinion gear) P4 and short gearion (third pinion gear) P3 meshing with sun gear S3 are in mesh with each other, and V is a loose Rabbi type planetary gear. is there.
- the sun gear S1 of the planetary gear DP is connected to the transmission case 3 (case 4 in a broad sense) and fixed in rotation.
- the carrier CR1 is connected to the input shaft 12. Subsequently, the rotation is the same as the rotation of the input shaft 12 (hereinafter referred to as “input rotation”), and it is connected to the second clutch C-2 (second input transmission clutch).
- the ring gear R1 is decelerated by reducing the input rotation by the fixed sun gear S1 and the input rotating carrier CR1, and the first clutch Cl (second deceleration transmission clutch) and It is connected to the third clutch C-3 (first deceleration transmission clutch).
- the sun gear S2 of the planetary gear unit PU is connected to the first brake B-1 and can be fixed to the mission case 3, and the rotation of the input shaft 12 is input via the intermediate shaft 13.
- the fourth clutch C-4 (first input transmission clutch) and the third clutch C-3 are connected to the third clutch C-3, and the input rotation of the input shaft 12 is transmitted via the fourth clutch C-4 to the third clutch.
- the ring gear R1's reduction rotational force can be input via C-3.
- the sun gear S3 is connected to the first clutch C1, and the reduced rotation of the ring gear R1 can be input.
- the carrier CR2 is connected to the second clutch C-2 so that the input rotation can be input via the second clutch C-2, and the second brake B-2 is connected to the second brake B-2. Connected to the second brake B-2, the rotation can be locked (fixed).
- the ring gear R3 is connected to the counter gear 15.
- a large-diameter gear 82 that meshes with the counter gear 15 is disposed at the left end of the counter shaft 81 of the counter shaft portion 80, and a small-diameter gear at the right end. 83 is arranged.
- a differential gear device 91 is disposed in the differential portion 90, and the diff ring gear 92 of the differential gear device 91 is meshed with the small diameter gear 83. That is, the rotation of the counter gear 15 is transmitted to the differential gear 92 of the differential gear device 91 via the large diameter gear 82, the counter shaft 81, and the small diameter gear 83, and the rotation of the differential gear 92 is transmitted to the differential gear 92.
- the device 91 transmits the left and right axles 931 and 93r while allowing a difference in rotational speed between the left and right axles 931 and 93r.
- FIG. 4 In the velocity diagram shown in FIG. 4, the vertical axis represents the rotational speed of each rotating element (each gear), and the horizontal axis represents the gear ratio of these rotating elements.
- the vertical axis at the end in the lateral direction (left side in FIG. 4) is the sun gear S1
- the vertical axis is the ring gear Rl, carrier in order from the right to the right in the figure. It corresponds to Lya CR1.
- the vertical axis at the lateral end is the sun gear S3 and thereafter, the vertical axis is the ring gear in order to the left.
- R3 R2
- CR3 carrier CR2
- sun gear S2 sun gear
- the first clutch C-1 and the third clutch C-3 are engaged. Then, as shown in FIG. 2 and FIG. 4, it is input to the sun gear S3 via the rotational force first clutch C-1 of the ring gear R1 that is decelerated and rotated by the fixed sun gear S1 and the carrier CR1 that is the input rotation. Further, the reduced rotation of the ring gear R1 is input to the sun gear S2 by the engagement of the third clutch C-3.
- the planetary gear unit PU is directly connected to the reduced rotation, and is output to the reduced rotation rotation gear R3 as it is, so that the forward rotation as the third forward speed is performed.
- the rotation is output from the counter gear 15.
- the fourth forward speed (4th) as shown in FIG. 3, the first clutch C-1 and the fourth clutch C-4 are engaged. Then, as shown in FIG. 2 and FIG. 4, it is input to the sun gear S3 via the rotational force first clutch C-1 of the ring gear R1 that is decelerated and rotated by the fixed sun gear S1 and the carrier CR1 that is the input rotation.
- the engagement of the fourth clutch C-4 causes the input rotation of the carrier CR1 to be input to the sun gear S2. Then, the carrier CR2 is decelerated and rotated at a higher speed than the sun gear S3, and the decelerated rotation input to the sun gear S3 is output to the ring gear R3 via the carrier CR2, and the forward rotation as the fourth forward speed is countered. Output from gear 15.
- the first clutch C-1, the second clutch C-2, the third clutch C-3, and the fourth clutch C-4 are released.
- the carrier CR1 and the sun gear S2 are disconnected
- the ring gear R1, the sun gear S2, and the sun gear S3, that is, the planetary gear DP and the planetary gear unit PU are disconnected.
- the input shaft 12 (intermediate shaft 13) and the carrier CR2 are disconnected.
- the power transmission between the input shaft 12 and the planetary gear unit PU is disconnected, that is, the power transmission between the input shaft 12 and the counter gear 15 is disconnected.
- FIG. 1 a schematic configuration of the entire automatic transmission 1 according to the first embodiment.
- the relative positional relationship between the components will be briefly described.
- clutch first to fourth clutch C1 to C4 and brake (first brake B-1 and second brake B-2) refer to friction. Used to include plates (external friction plates and internal friction plates) and hydraulic servos that connect and disconnect them.
- the automatic transmission 1 includes a transmission mechanism 2 in a mission case 3.
- the planetary gear unit PU is disposed on the intermediate shaft 13
- the second clutch C is arranged on the right side (input side) in the axial direction of the planetary gear unit PU in order from the right side.
- 1st clutch C—1, planetary gear DP, 3rd clutch C—3, and power counter gear 15 are arranged.
- a fourth clutch C-4 and a first brake B-1 are arranged on the left side in the axial direction of the planetary gear unit PU.
- a second brake B-2 is arranged on the outer peripheral side of the planetary gear unit PU.
- the friction plate 31 of the second clutch C-2 is arranged on the input shaft 12 on the right inner side of the mission case 3, that is, on the right side of the counter gear 15, in order from the right side.
- the friction plate 21 of the first clutch C-1 and the friction plate 41 of the third clutch C-3 are disposed on the relatively outer diameter side in the transmission case 3.
- a partition member 3a that separates between the transmission case 3 and a housing case (not shown) is fixed to the transmission case 3 as a part of the case 4, and is connected to the partition member 3a.
- the hydraulic servo 30 of the second clutch C-2 is disposed on the boss portion 3b (the boss portion 3b may not be integral with the partition wall member 3a).
- the hydraulic servo 20 of the first clutch C-1 is disposed on the left side of the hydraulic servo 30, the hydraulic servo 20 of the first clutch C-1 is disposed.
- the planetary gear DP force and on the inner diameter side of the friction plate 41 are arranged. Is provided with a hydraulic servo 40 for the third clutch C-3.
- the hydraulic servo 30, hydraulic servo 20, and planetary gear DP are arranged in order on the boss 3b on the right side of the mission case 3 (the base side force of the boss 3b is also in the axial direction to the left).
- the hydraulic servo 40 is arranged on the input shaft 12 so as to be adjacent to the planetary gear DP.
- a flange-like support wall (center support member) 120 is fixedly disposed on the inner peripheral surface of the transmission case 3, On the inner diameter side of the support wall 120, a sleeve-shaped support portion 120a is disposed.
- a counter gear 15 connected to a ring gear R3 of a planetary gear unit PU, which will be described later, via a ball bearing 121 is rotatably supported by the support wall 120! RU
- a planetary gear unit PU is disposed on the intermediate shaft 13 on the left side of the transmission case 3 in the drawing, that is, on the left side of the counter gear 15.
- a friction plate 71 of the second brake B-2 and a hydraulic servo 70 of the second brake B-2 are disposed on the right side of the outer peripheral side of the planetary gear unit PU, and the outer diameter side of the planetary gear unit PU.
- a friction plate 61 of the first brake B-1 is disposed on the left side of the first brake B-1.
- a friction plate 51 of the fourth clutch C-4 is disposed on the left side of the friction plate 61, and a hydraulic servo 60 of the first brake B-1 is disposed on the left side of the friction plate 51. It is installed.
- a hydraulic servo 50 for the fourth clutch C-4 is disposed on the inner peripheral side of the hydraulic servo 60.
- the hydraulic servo 30 of the second clutch C-2 and the hydraulic servo 20 of the first clutch C-1 are arranged on the opposite side to the planetary gear set PU in the axial direction with respect to the planetary gear DP.
- the hydraulic servo 40 of the third clutch C-3 and the counter gear 15 are arranged between the planetary gear DP and the planetary gear set PU in the axial direction.
- the hydraulic servo 60 is arranged on the side opposite to the planetary gear DP in the axial direction with respect to the planetary gear unit PU.
- the planetary gear DP arranged inside the mission case 3 includes a sun gear S1, a carrier CR1, and a ring gear R1.
- the sun gear S1 is non-rotatably fixed to the boss portion 3b connected to the partition wall member 3a.
- the carrier CR1 has two carrier plates in the left-right direction, and rotatably supports the pions PI and P2.
- the pinions PI and P2 are combined with each other, the former pinion P1 is combined with the sun gear S1, and the latter pinion P2 is combined with the ring gear R1.
- the left carrier plate is connected to the input shaft 12, and the right carrier plate is a clutch drum 32 that spline-engages the outer friction plate 31 of the second clutch C-2 friction plate 31.
- Ring gear R1 has an inner friction plate on the outer circumferential surface of friction plate 21 of first clutch C-1. Pline engagement.
- a hub member 113 is coupled to the left side of the ring gear R1, and the inner friction plate of the friction plate 41 of the third clutch C-3 is spline engaged with the hub member 113.
- the first clutch C-1 includes a friction plate 21 and a hydraulic servo 20 that connects and disconnects the friction plate 21.
- the hydraulic servo 20 has a clutch drum 22, a piston member 23, a cancel plate 24, and a return spring 25, and these constitute an oil chamber 26 and a cancel oil chamber 27.
- the clutch drum 22 has an inner diameter portion arranged on the outer peripheral side of the inner diameter portion of the clutch drum 32 of the second clutch C-2, and an outer friction plate force of the friction plate 21 on the inner peripheral surface of the outer diameter portion S spline
- the distal end of the outer diameter portion is connected to a transmission member 102 that passes through the inner peripheral side of the counter gear 15 and is connected to a sun gear S3 of a planetary gear unit PU described later.
- the inner friction plate of the friction plate 21 is spline-engaged with the outer peripheral side of the ring gear R1 and the hub member 111 extending from the ring gear R1.
- the piston member 23 is disposed on the left side of the clutch drum 22 so as to be movable in the axial direction, and forms a nectar-shaped oil chamber 26 between the seal ring al and a2 and the clutch drum 22. ing. Further, the cancel plate 24 is prevented from moving leftward by a snap ring 29 fitted to the clutch drum 22 described above.
- the cancel plate 24 has a return spring 25 contracted between the piston member 23 arranged on the right side of the cancel plate 24 and a nectar-like cancel oil chamber 27 by the seal rings al and a3.
- the second clutch C 2 is disposed on the right side of the first clutch C 1 and is disposed on the boss portion 3b.
- the second clutch C-2 includes a friction plate 31 and a hydraulic servo 30 for connecting and disconnecting the friction plate 31.
- the hydraulic servo 30 includes a clutch drum 32, a piston member 33, a cancel plate 34, and a return spring 35, and these constitute an oil chamber 36 and a cancel oil chamber 37.
- the clutch drum 32 has a left end of the inner diameter portion connected to the carrier CR1 of the planetary gear DP, and the hydraulic servo 20 of the first clutch C 1 described above is disposed on the outer peripheral portion on the left side.
- the hydraulic servo 30 is included on the right side.
- the outer friction plate force S of the friction plate 31 is S-spline engaged, and the inner friction plate of the friction plate 31 is spline-engaged with the hub member 112.
- This hub member 112 passes through the outer periphery of the first clutch C-1, the planetary gear DP, and the third clutch C3, and passes through the inner periphery of the counter gear 15 to the right of the carrier CR2 of the planetary gear unit PU described later. It is connected to the transmission member 103 connected to the side plate on the other side (that is, the planetary gear DP side).
- the piston member 33 is disposed on the left side of the clutch drum 32 so as to be movable in the axial direction, and a seal-like oil chamber 36 is formed between the piston member 33 and the clutch drum 32 by the seal rings a4 and a5. Yes. Further, the cancel plate 34 is prevented from moving leftward by the snap ring 39 fitted to the clutch drum 32 described above. Between the cancel plate 34 and the piston member 33 arranged on the right side of the cancel plate 34, a return spring 35 is contracted and a nail-like cancel oil chamber 37 is configured by the seal rings a4 and a6. .
- the clutch drum 32 of the second clutch C-2 is connected to the input shaft 12 via the carrier CR1, that is, rotates with the same input rotation as the input shaft 12, so that the clutch drum 32
- An input rotation speed sensor that measures the input rotation speed can be provided on the outer periphery of the input shaft.
- the input rotation speed sensor can be easily input compared to the case where the input rotation speed sensor is provided at a position where the rotation of the input shaft 12 can be directly measured.
- a number sensor can be attached.
- the third clutch C-3 is located on the left side of the planetary gear DP and is disposed on the input shaft 12.
- the third clutch C-3 includes a friction plate 41 and a hydraulic servo 40 that connects and disconnects the friction plate 41. I have.
- the inner friction plate of the friction plate 41 is spline-engaged with the outer peripheral surface of the knob member 113 connected to the ring gear R1. Further, the outer friction plate of the friction plate 41 is spline-engaged with an inner peripheral side of a clutch drum 42 described later, and the clutch drum 42 passes through the inner peripheral side of the counter gear 15 to the sun gear S2 of the planetary gear unit PU. It is connected to the connected transmission member 101.
- the hydraulic servo 40 includes a clutch drum 42, a piston member 43, a cancel plate 44, and a return spring 45, and these constitute an oil chamber 46 and a cancel oil chamber 47.
- the clutch drum 42 is attached to the left outer peripheral surface of the input shaft 12 so as to be relatively rotatable.
- the piston member 43 is disposed on the clutch drum 42 so as to be movable in the axial direction, and an oil chamber 46 is formed between the piston drum 43 and the clutch drum 42 by seal rings a7 and a8. ing.
- the piston member 43 has an outer peripheral portion facing the front surface of the friction plate 41.
- cancel plate 44 is prevented from moving to the right side by the snap ring 49 fitted to the outer peripheral surface on the inner diameter side of the clutch drum 42 described above, and the piston member 43 disposed on the left side thereof In between, the return spring 45 is contracted and the nail-like cancel oil chamber 47 is constituted by the seal rings a 7 and a 9.
- the first brake B-1 is arranged so that the outer diameter side force of the left portion of the planetary gear unit PU extends to the side wall portion 3c of the transmission case 3 on the left side.
- the first brake B-1 includes a friction plate 61 and a hydraulic servo 60 that connects and disconnects the friction plate 61.
- the outer friction plate of the friction plate 61 is spline-engaged with the inner peripheral surface of the transmission case 3, and the inner friction plate is connected to a nove member 116 connected to the sun gear S2 of the planetary gear unit PU via the transmission member 104. The spline is engaged.
- the hydraulic servo 60 includes a piston member 63, a cancel plate 64, and a return spring 65, and an oil chamber 66 is configured between the piston member 63 and the transmission case 3.
- the piston member 63 is disposed so as to be movable in the axial direction, and the right side end portion faces the friction plate 61.
- An oil chamber 66 is formed between the piston member 63 and the transmission case 3 by two seal rings al3 and al4. Further, the cancel plate 64 is prevented from moving rightward by a snap ring 69 fitted to the inner peripheral surface of the mission case 3.
- Second brake B-2 is arranged on the outer diameter side of ring gear R3 of planetary gear unit PU.
- the second brake B-2 includes a friction plate 71 and a hydraulic servo 70 for connecting and disconnecting the friction plate 71.
- the outer friction plate of the friction plate 71 is splined to the inner peripheral surface of the transmission case 3, and the inner friction plate is splined to the hub member 117 connected to the carrier CR2 of the planetary gear unit PU. .
- the hydraulic servo 70 includes a cylinder member 72, a piston member 73, a cancel plate 74, and a return spring 75, and an oil chamber 76 is formed between the cylinder member 72 and the piston member 73.
- the piston member 73 is disposed so as to be movable in the axial direction, and the right side end portion faces the friction plate 71.
- An oil chamber 76 is formed between the piston member 73 and the transmission case 3 by two seal rings al5 and al6. Cancel further The plate 74 is prevented from moving to the right by a snap ring 79 fitted to the inner peripheral surface of the mission case 3.
- the fourth clutch C-4 is disposed on the left side of the planetary gear unit PU and on the inner diameter side of the first brake B-1.
- the friction plate 51 and the friction plate 51 are in contact with each other. It has a hydraulic servo 50 that cuts off.
- the inner friction plate of the friction plate 51 is connected to the hub member 116 described above and is spline-engaged with the hub member 114 connected to the carrier CR2 via the transmission member 104. Further, the outer friction plate of the friction plate 51 is spline-engaged with an inner peripheral side of a clutch drum 52 described later, and the clutch drum 52 is connected to the intermediate shaft 13.
- the intermediate shaft 13 is spline-engaged with the input shaft 12 described above, that is, the clutch drum 52 is connected to the input shaft 12 via the intermediate shaft 13.
- the fourth clutch C-4 enables the direct input shaft 12 (intermediate shaft 13) and the sun gear S2 to be engaged and disengaged through the carrier CR1 of the planetary gear DP, for example.
- the hydraulic servo 50 includes a clutch drum 52, a piston member 53, a cancel plate 54, and a return spring 55, and these constitute an oil chamber 56 and a cancel oil chamber 57.
- the clutch drum 52 has an inner peripheral right end attached to the intermediate shaft 13 and is rotatably supported on a boss 3d connected to the side wall 3c of the transmission case 3.
- the piston member 53 is disposed on the clutch drum 52 so as to be movable in the axial direction.
- An oil chamber 56 is formed between the piston member 53 and the clutch drum 52 by the seal rings alO, all.
- the piston member 53 has an outer peripheral portion facing the front surface of the friction plate 51.
- cancel plate 54 is prevented from moving to the right side by the snap ring 59 fitted to the outer peripheral surface on the inner diameter side of the clutch drum 52 described above, and the piston disposed on the left side thereof is blocked.
- a return spring 55 is contracted between the member 53 and a nectar-like cancel oil chamber 57 is constituted by the seal rings alO and al2.
- the planetary gear unit PU includes a sun gear S2, a sun gear S3, a short pinion P3 meshing with the sun gear S3, a long pinion P4 meshing with the sun gear S2, the short pinion P3, and the ring gear R3, Consists of a loose Ravio-type planetary gear that has a carrier CR2 that rotatably supports the short beon P3 and long pion P4 by both side plates, and a ring gear R3 that mates with the long pion P4. It has been.
- the sun gear S2 is connected to the transmission member 101 that passes through the inner peripheral side of the counter gear 15 on the right side, and is connected to the clutch drum 42 of the third clutch C-3 via the transmission member 101. It is connected.
- the sun gear S2 is connected to the transmission member 104 on the left side, and the hub member 114 of the fourth clutch C-4 and the hub member 116 of the first brake B-1 are connected via the transmission member 104. It is connected.
- the transmission member 102 passing through the inner peripheral side of the counter gear 15 is connected to the right side, and the clutch drum 22 of the first clutch C-1 is connected through the connection member 102. .
- a side plate on the right side that is, the planetary gear DP side, is connected to a transmission member 103 that passes through the inner peripheral side of the counter gear 15 described above, and the second clutch C is connected via the transmission member 103.
- the carrier CR2 has a left side plate connected to the hub member 117 of the second brake B-2.
- the ring gear R3 is coupled to the counter gear 15 via the transmission member 105.
- the counter gear 15 is combined with the large-diameter gear 82 connected to the counter shaft 81 as described above, and the left and right axles 931, 93r (through the counter shaft portion 80, the differential gear portion 90, etc. That is, it is connected to the drive wheel.
- the oil chamber 36 of the hydraulic servo 30 of the second clutch C 2 that is, the oil chamber 36 formed by sealing between the clutch drum 32 and the piston member 33 by seal rings a4 and a5, includes the clutch drum 32 and the boss.
- the oil passage c30 in the boss portion 3b communicates with the seal ring dl, d2 between the portion 3b and hydraulic oil is supplied from the oil passage c30.
- Oil is also supplied to the cancel oil chamber 37 (not shown) that is configured by sealing between the piston member 33 and the cancel plate 34 by seal rings a4 and a6.
- the oil chamber 26 of the hydraulic servo 20 of the first clutch C-1 that is, the oil chamber 26 formed by sealing the gap between the clutch drum 22 and the piston member 23 with seal rings al and a2,
- the seal ring d3, d4 between the clutch drum 32 and the boss 3b of the second clutch C-2 and the seal ring d5, d6 between the clutch drum 32 and the clutch drum 22 are respectively provided.
- the oil passage c20 in the boss portion 3b is communicated with the seal, and hydraulic oil is supplied from the oil passage c20.
- Seal ring al, a3 between piston member 23 and cancel plate 24 Oil is supplied from a not-shown oil passage to the cancel oil chamber 27 which is sealed by the oil.
- the oil chamber 46 of the hydraulic servo 40 of the third clutch C 3 that is, the oil chamber 46 constituted by sealing the gap between the clutch drum 42 and the piston member 43 with seal rings a7, a8, Between the boss ⁇ 3b and the manpower shaft 12 is sealed with d7 and d8, and between the manpower shaft 12 and the clutch drum 42 is sealed with seal rings d9 and dlO, and the oil passage c40 in the boss 3b is connected to the input shaft.
- the oil passages c41, c42, and c43 in the cylinder 12 communicate with each other, and hydraulic oil is supplied from the oil passage c43.
- oil is supplied from an oil passage (not shown) to a cancel oil chamber 47 configured to be sealed between the piston member 43 and the cancel plate 44 by seal rings a7 and a9.
- the oil chamber 56 of the hydraulic servo 50 of the fourth clutch C-4 that is, the oil chamber 56 configured to be sealed between the clutch drum 52 and the piston member 53 by seal rings alO and all. Is sealed between the clutch drum 52 and the boss portion 3d by the seal rings dl l and dl2, and the oil passage c50 in the boss portion 3d communicates, and hydraulic oil is supplied from the oil passage c50. Note that oil is supplied from an oil passage (not shown) to a cancel oil chamber 57 that is configured to be sealed between the piston member 53 and the cancel plate 54 by seal rings alO and al2.
- the oil chamber 66 of the hydraulic servo 60 of the first brake B-1 that is, the oil constituted by sealing the space between the side wall 3c of the transmission case 3 and the piston member 63 with seal rings al3 and al4.
- the hydraulic oil is also supplied to the chamber 66 in the oil passage of the side wall 3c (not shown).
- the oil chamber 76 of the hydraulic servo 70 of the second brake B-2 that is, the oil chamber 76 formed by sealing the cylinder member 72 and the piston member 73 with seal rings al5 and al6,
- the oil passage force hydraulic oil in the transmission case 3 (not shown) is supplied.
- an oil passage c80 is formed in the input shaft 12 and the intermediate shaft 13 in the axial direction, and the oil passage c80 includes an oil passage cap (not shown) in the boss portion 3b or the boss portion 3d. Also, lubricant is supplied.
- the input shaft 12 and the intermediate shaft 13 are provided with a plurality of holes (not shown) from the oil passage 80 in the radial direction, and the lubricating oil supplied to the oil passage c80 is scattered from these holes. In this form, it is supplied into the transmission mechanism 2
- an oil passage c90 is formed in the input shaft 12 in the axial direction.
- the oil passage 90 is not shown.
- the hydraulic fluid is connected to the lockup clutch 10 through the oil passage.
- the hydraulic oil is supplied to the friction plate of the lock-up clutch 10 and presses the friction plate to engage the lock-up clutch 10.
- an input rotation element of a reduction planetary gear and a rotation element of a planetary gear set are engaged via a clutch.
- the transmission member that transmits the input rotation is connected to the rotating element of the planetary gear set through the radial outer peripheral side of the planetary gear set.
- the rotating gear element is connected to the rotating element so as to wrap around the planetary gear set.
- the transmission member wraps the planetary gear set for the reduction planetary gear, it is difficult to assemble the vehicle automatic transmission. Further, for example, even if the transmission member is divided into a plurality of parts and connected by splines or the like, the splines are aligned and assembled, and it is difficult to easily assemble the vehicle automatic transmission.
- the transmission member also wraps other clutches, for example, a center support member is provided to supply hydraulic fluid for the center support member force clutch.
- the hydraulic servos of such clutches need to be supplied with hydraulic fluid from the input shaft (particularly via a relative rotating member).
- the number of seal rings increases and sliding resistance increases, which hinders improvement in power transmission efficiency of the vehicle automatic transmission.
- the fourth clutch C-4 is arranged so as to be interposed on the transmission path connecting the input shaft 12 and the sun gear S2
- the second clutch C-2 is disposed so as to be interposed on the transmission path connecting the carrier CR1 and the carrier CR2, and the output side transmission member 103 of the second clutch C-2 is arranged in the axial direction of the planetary gear unit PU. Since the planetary gear DP is connected to the carrier CR2, the member for enclosing the planetary gear unit PU can be eliminated. As a result, the radial compactness of the vehicle automatic transmission 1 can be achieved.
- the transmission member that requires high rigidity can be shortened, the weight can be reduced, and the controllability of the vehicle automatic transmission 1 can be improved. Furthermore, it can be configured to easily discharge the supplied lubricating oil, and cooling performance can be ensured. In addition, the assembly of the vehicle automatic transmission 1 can be facilitated. Furthermore, depending on the arrangement structure of each clutch, the support wall 120 can be provided to enable the configuration in which the hydraulic fluid of the clutch is supplied from the support wall 120, so that the number of seal rings can be reduced. As a result, the sliding resistance of the seal ring can be reduced, and the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- a counter gear 15 connected to the ring gear R3 is provided, and the counter gear 15 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, and the output side member of the third clutch C-3 101, the output-side transmission member 102 of the first clutch C-1 and the output-side transmission member 103 of the second clutch C-2 are connected to the planetary gear PU through the inner peripheral side of the counter gear 15. Therefore, the counter gear 15 can be arranged between the planetary gear unit PU and the planetary gear DP in the axial direction, and the vehicle automatic transmission 1 can be suitably used for an FF type vehicle. .
- the hydraulic servo 30 of the second clutch C-2 is arranged on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, the hydraulic servo 30 of the second clutch C-2 is connected to the hydraulic servo 30 of the case 4.
- Supply hydraulic fluid from oil passage c30 provided in boss 3b connected to one end Can be possible.
- the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil.
- the power transmission efficiency of the transmission 1 can be improved.
- the friction plate 51 of the fourth clutch C 4 is relatively outer circumferential. Since the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be ensured, and the number of the friction plates 51 can be reduced. Furthermore, hydraulic oil can be supplied to the hydraulic servo 50 of the fourth clutch C-4 from an oil passage c50 provided in the boss portion 3d connected to one end of the case 4. As a result, the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal ring as compared with the case of supplying hydraulic oil. The power transmission efficiency of the transmission can be improved.
- the hydraulic servo 40 of the third clutch C-3 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, the planetary gear PU is opposite to the planetary gear PU in the axial direction.
- the distance between the third clutch C-3 and the planetary gear unit PU can be shortened compared to the case where it is arranged on the side, and the strength of the third clutch C-3, which requires strength to transmit high torque, can be reduced.
- the output side transmission member 101 can be shortened. As a result, it is possible to achieve light weight and improve controllability as the vehicle automatic transmission 1.
- the hydraulic servo 20 of the first clutch C-1 is arranged on the opposite side of the planetary gear unit PU in the axial direction with respect to the planetary gear DP, the hydraulic servo 20 of the first clutch C-1 is connected to the hydraulic servo 20 of the case 4. It is possible to supply hydraulic oil from an oil passage c20 provided in the boss portion 3b connected to one end. As a result, for example, the hydraulic path 20 can be shortened compared to the case where the hydraulic servo 20 of the first clutch C-1 is disposed on the input shaft 12 and hydraulic oil is supplied via the input shaft 12. As a vehicle automatic transmission 1, controllability can be improved.
- the first brake B-1 that can freely lock the rotation of the sun gear S2 with respect to the case 4 is provided. Since the hydraulic servo 60 of the first brake B-1 is arranged on the opposite side of the planetary gear DP with respect to the planetary gear unit PU, the locking force transmission member of the first brake B-1 and the sun gear S2 are The automatic transmission 1 for a vehicle can be made compact.
- the transmission member 103 on the output side of the second clutch C-2 has the third and first clutches C-3, C-1 Are connected to the carrier CR2 through the outer peripheral side of the output side transmission members 101 and 102, and the output side transmission member 104 of the fourth clutch C-4 and the output side transmission member 101 of the third clutch C-3 are The transmission member 104 on the output side of the fourth clutch C 4, which is coupled to the sun gear S2 and rotates integrally therewith, the transmission member 101 on the output side of the third clutch C-3, and the sun gear S2 are connected to the first clutch.
- the output side of the fourth clutch C—4 that rotates faster than the transmission member 103 on the output side of the second clutch C-2
- the transmission member 104 of the first clutch C 1 is located on the inner peripheral side of the transmission member 103 on the output side of the second clutch C-2.
- the diameter of the transmission member 104 on the output side of the fourth clutch C-4 can be made smaller than the diameter of the transmission member 103 on the output side of the second clutch C-2.
- the third and first clutches C-3, C-1 are arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the outputs of the third and first clutches C-3, C-1 are provided.
- Side transmission members 101 and 102 are connected to the sun gear S2 and sun gear S3, respectively, and the fourth clutch C-4 is arranged on the side opposite to the planetary gear DP in the axial direction with respect to the planetary gear unit PU.
- the transmission member 104 on the output side of C-4 is connected to the sun gear S2, and the second clutch C2 is arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the transmission member on the output side of the second clutch C-2 103 is connected to the carrier CR2 through the outer peripheral side of the output members 101, 102 on the output side of the third and first clutches C-3, C-1, so that the output on the output side of the second clutch C-2 is transmitted.
- Fourth clutch C 4 with higher rotation than member 103 Since the output side transmission member 104 is on the inner peripheral side, the output side transmission member of the fourth clutch C 4 The diameter of the reach member 104 can be made smaller than the diameter of the transmission member 103 on the output side of the second clutch C-2, and a lighter weight can be achieved than when it is on the outer peripheral side. In addition, since inertia (inertia force) can be reduced as compared with the case of the outside, the vehicle automatic transmission 1 can improve control performance.
- the friction plate 51 of the fourth clutch C-4 is arranged relatively on the outer peripheral side compared to the hydraulic servo 50 of the fourth clutch C4 arranged between the planetary gear unit PU and the planetary gear DP. Since the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of the friction plates 51 can be reduced. In addition, the distance between the third and first clutches C-3, C-1 and the planetary gear unit PU can be shortened, and the third and first clutches C-3, which are strong enough to transmit high torque, are required. , C-1 output side transmission members 101 and 102 can be shortened. As a result, a light weight can be achieved, and the controllability of the vehicle automatic transmission 1 can be improved.
- hydraulic oil can be supplied to the hydraulic servo 50 of the fourth clutch C-4 from, for example, an oil passage c50 provided in the boss portion 3b connected to the side wall 3a of the case 4. .
- the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal ring as compared with the case of supplying hydraulic oil. The power transmission efficiency of the transmission can be improved.
- the transmission member on the input side of the fourth clutch C-4 it is connected to the input shaft 12 and the intermediate shaft 13 that pass through the inner peripheral side of the planetary gear unit PU, and the transmission on the input side of the fourth clutch C4.
- Part of the member is configured as the clutch drum 52 of the hydraulic servo 50 of the fourth clutch C—4, so that the transmission member on the output side of the fourth clutch C—4 is configured as the clutch drum of the hydraulic servo 50. Since the clutch drum of the hydraulic servo 50 can also serve as a power transmission member from the input shaft 12, it can be configured compactly in the axial direction.
- the hydraulic servo 30 of the second clutch C-2 is disposed on the input shaft 12 away from the boss portion 3b and hydraulic oil is supplied through the oil passage in the input shaft 12.
- the oil path length can be shortened by the amount that the oil path in the input shaft 12 is not interposed, so that the controllability of the vehicle automatic transmission 1 can be improved.
- the hub member 111 of the first clutch C-1 is connected to the ring gear R1, the output transmission member 102 of the first clutch C-1 is connected to the sun gear S3, and the first clutch C- A part of the output member 102 on the output side of 1 is configured as a clutch drum 22 of the hydraulic servo 20 of the first clutch C—1, and the hydraulic servo 20 is composed of the planetary gear DP and the hydraulic servo 20 of the second clutch C—1.
- the hydraulic axis 20 and the hydraulic servo 20 of the first clutch C-1 from the oil passage c20 provided in the boss 3b connected to the side wall 3a of the case 4. Can be made available.
- the hydraulic servo 20 of the first clutch C-1 is disposed on the input shaft 12 away from the boss 3b, and hydraulic oil is supplied through the oil passage in the input shaft 12.
- the length of the oil passage can be shortened by not interposing the oil passage in the input shaft 12, and the controllability of the vehicle automatic transmission 1 can be improved.
- the counter shaft 81 is arranged in parallel to the input shaft 12 and connected via the counter gear 15 connected to the ring gear R3, and the output rotation from the ring gear R3 1S via the counter gear 15 is provided. Since it is transmitted to the counter shaft 81, the vehicle automatic transmission 1 can be suitably used for an FF type vehicle.
- the counter gear 15 is arranged between the planetary gear unit PU and the planetary gear DP in the axial direction, and is supported by the support portion 120a connected to the support wall 120 extending from the case 4,
- the counter gear 15 can be prevented from moving away from the input side force in the axial direction.
- the counter shaft portion 80 and the differential gear portion 90 can be brought closer to the torque converter 7 side, so that the vehicle automatic transmission 1 can be compacted.
- the carrier CR1 is connected to the input shaft 12 on the planetary gear unit PU side with respect to the planetary gear DP, and the second clutch C is connected to the planetary gear DP on the side opposite to the planetary gear unit PU in the axial direction.
- the clutch drum 32 which is the transmission member on the input side of 2
- the transmission member 32 on the input side of the carrier CR1 and the second clutch C 2 and the input shaft 12 can be connected without complicating the members.
- the vehicle automatic transmission 1 can be connected.
- the hub member 116 of the first brake B-1 and the transmission member 104 connected thereto are connected to the gear S2 on the opposite side in the axial direction from the planetary gear DP in the planetary gear unit PU,
- the hub member 116 and the transmission member 104 of the brake B-1 and the sun gear S2 can be connected without complicating the members, and the vehicle automatic transmission 1 can be connected.
- the planetary gear DP supports the sun gear S1 whose rotation is always fixed with respect to the case 4, the pin-on gear P1, and the pin-on gear P2 rotatably, and is always connected to the input shaft 12. Since it comprises CR1 and a ring gear R1 that meshes with the pinion gear P2 and outputs a reduced speed rotation, it is possible to output a reduced speed rotation that reduces the input rotation of the input shaft 12 from the ring gear R1.
- the planetary gear unit PU includes a sun gear S2, a sun gear S3, a short pinion P3 that meshes with the sun gear S3, a long pinion P4 that meshes with the sun gear S2, and meshes with the short peer P3, Since each of the planetary gear units PU is comprised of a radio gear type planetary gear unit PU having a carrier CR2 that rotatably supports the short pinion P3 and the long pinion P4 and a ring gear R3 that meshes with the long pinion P4. While it is possible to connect the rotating element and the output side member of each clutch or brake without complicating the members, the high rotating speed of each rotating element can be prevented and a good gear ratio can be obtained. be able to.
- Engaging the 6th forward speed By engaging the 6th forward speed, the second clutch C-2 and the third clutch C-3 are engaged, the 7th forward speed is engaged, the second clutch C-2 is engaged, and the first brake B -Locking 1 to move forward 8th gear, engaging 3rd clutch C-3 or 4 clutch C-4 and locking 2nd brake B-2 Each can be achieved.
- the vertical axis indicates the rotational speeds of the sun gear S2, sun gear S3, carrier CR2, and ring gear R3 of the planetary gear unit PU
- the horizontal axis indicates the gears of the sun gear S2, sun gear S3, carrier CR2, and ring gear R3.
- the sun gear S2 is positioned at the end of the lateral direction, and is configured correspondingly to the carrier CR2, the ring gear R3 connected to the counter gear 15, and the sun gear S3 in this order. Can do.
- vehicle automatic transmission 1 is configured so that the speed change mechanism 2 is
- FIG. 5 is a sectional view showing the automatic transmission 1 according to the second embodiment.
- the automatic transmission 1 according to the second embodiment is the same as the automatic transmission 1 according to the first embodiment.
- the hydraulic servo 30 of the second clutch C 2 is repositioned between the planetary gear DP and the planetary gear PU in the axial direction.
- the hydraulic servo 30 of the second clutch C-2 is It is configured so as to be adjacent to the support wall 120 between the axial direction of the gear 15 and the hydraulic servo 40 of the third clutch C-3.
- the hydraulic servo 20 of the first clutch C 1 is connected to the planetary gear.
- the planetary gear unit PU is arranged on the opposite side of the shaft in the axial direction with respect to the DP. It is arranged between the net gear DP and the planetary gear unit PU in the axial direction. Located on the opposite side.
- the fourth clutch C-4 is connected to the input shaft 12 and the sun gear.
- the second clutch C-2 is placed on the transmission path connecting between the carrier CR1 and the carrier CR2, and the second clutch C-2 is arranged on the transmission path connecting to the S2. Since the output transmission member 103 of the clutch C-2 is connected to the carrier CR2 on the planetary gear DP side in the axial direction of the planetary gear unit PU, a member for enclosing the planetary gear unit PU can be eliminated. As a result, the automatic transmission 1 for the vehicle
- a support wall 120 can be provided to enable the configuration in which the hydraulic fluid for the clutch is supplied from the support wall 120, thereby reducing the number of seal rings. Therefore, the sliding resistance of the seal ring can be reduced, and the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- the support wall 120 is connected to the hydraulic servo 30 of the second clutch C2.
- the oil passage provided inside can also be able to supply hydraulic oil.
- the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case where hydraulic oil is supplied.
- the power transmission efficiency as the dynamic transmission 1 can be improved.
- the friction plate 51 of the fourth clutch C4 is relatively outer circumferential. Since the friction plate 51 can be arranged on the side and the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be ensured, and the number of friction plates can be reduced.
- a bolt connected to one end of the case 4 is connected to the hydraulic servo 50 of the fourth clutch C-4.
- the oil passage power provided in the support portion 3d can also supply hydraulic oil. As a result, the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. The power transmission efficiency of the automatic transmission 1 can be improved.
- the hydraulic servo 40 of the third clutch C 3 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, the planetary gear PU is opposite to the planetary gear PU with respect to the planetary gear DP.
- the output of the third clutch C-3 which can shorten the distance between the third clutch C-3 and the planetary gear unit PU and requires strength to transmit high torque,
- the side transmission member 101 can be shortened. As a result, it is possible to achieve light weight and improve controllability as the vehicle automatic transmission 1.
- the hydraulic servo 20 of the first clutch C-1 is disposed on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, the hydraulic servo 20 of the first clutch C-1 is It is possible to supply oil passage force hydraulic oil provided in the boss 3b connected to one end. As a result, the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. To improve power transmission efficiency as an automatic transmission 1
- the first brake B-1 that can freely lock the rotation of the sun gear S2 with respect to the case 4 is provided, and the hydraulic servo 60 of the first brake B-1 is connected to the planetary gear unit PU with the planetary gear DP. Since it is arranged on the opposite side in the axial direction, the locking force transmission member of the first brake B-1 and the sun gear S2 can be connected without complicating the members.
- the second clutch C-2 As described above, according to the vehicle automatic transmission 1 according to the present invention, the second clutch C-2
- the output-side transmission member 103 is connected to the carrier CR2 through the outer peripheral side of the output-side transmission members 101, 102 of the third and first clutches C-3, C-1, and the fourth clutch C-4.
- the output side transmission member 104 and the output side transmission member 101 of the third clutch C-3 are connected to the sun gear S2, and the output side transmission member of the fourth clutch C4 that rotates integrally therewith.
- the diameter of the output member 104 on the output side of the second clutch C-2 is set to the diameter of the output member 104 on the output side of the second clutch C-2. The diameter can be made smaller than the diameter, and the weight can be reduced compared to the case where it is arranged on the outer peripheral side. In addition, since inertia (inertial force) can be reduced as compared with the case where it is arranged on the outer peripheral side, the controllability of the vehicle automatic transmission 1 can be improved.
- the third and first clutches C-3, C-1 are arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the outputs of the third and first clutches C-3, C-1 are provided.
- Side transmission members 101 and 102 are connected to the sun gear S2 and sun gear S3, respectively, and the fourth clutch C-4 is arranged on the side opposite to the planetary gear DP in the axial direction with respect to the planetary gear unit PU.
- the transmission member 104 on the output side of C-4 is connected to the sun gear S2, and the second clutch C2 is arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the transmission member on the output side of the second clutch C-2 103 is connected to the carrier CR2 through the outer peripheral sides of the output members 101, 102 on the output side of the third and first clutches C-3, C-1, so that the output on the output side of the second clutch C-2 is transmitted.
- 4th clutch C with higher rotation than member 103 Since the output member 104 on the output side 4 is the inner peripheral side, the diameter of the output member 104 on the output side of the fourth clutch C 4 is larger than the diameter of the output member 103 on the output side of the second clutch C-2. It can be made smaller and lighter than the outer peripheral side.
- the inertia inertial force
- the friction plate 51 of the fourth clutch C-4 is arranged relatively on the outer peripheral side compared to the hydraulic servo 50 of the fourth clutch C4 arranged between the planetary gear unit PU and the planetary gear DP. Since the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of the friction plates 51 can be reduced. In addition, shorten the distance between the 3rd and 1st clutches C-3, C-1 and the planetary gear unit PU. Therefore, the transmission members 101 and 102 on the output side of the third and first clutches C-3 and C-1 that need strength to transmit high torque can be shortened. As a result, a light weight can be achieved, and the controllability of the vehicle automatic transmission 1 can be improved.
- the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal ring as compared with the case of supplying hydraulic oil.
- the power transmission efficiency of the transmission 1 can be improved.
- the transmission member on the input side of the fourth clutch C-4 it is connected to the input shaft 12 and the intermediate shaft 13 that pass through the inner peripheral side of the planetary gear unit PU, and the transmission on the input side of the fourth clutch C4.
- Part of the member is configured as the clutch drum 52 of the hydraulic servo 50 of the fourth clutch C—4, so that the transmission member on the output side of the fourth clutch C—4 is configured as the clutch drum of the hydraulic servo 50. Since the clutch drum of the hydraulic servo 50 can also serve as a power transmission member from the input shaft 12, it can be configured compactly in the axial direction.
- the counter gear 15 is connected to the ring gear R3 and is arranged between the planetary gear unit PU and the planetary gear DP in the axial direction.
- the counter gear 15 is connected to the support wall 120 extending from the case 4, and the counter gear. 15 and supporting the hub member 112 of the second clutch C-2 through the outer peripheral side of the third and first clutches C-3, C-1, and to the carrier CR1,
- a part of the transmission member 103 on the output side of the second clutch C-2 is configured as a clutch drum 32 of the hydraulic servo 30 of the second clutch C-2, and the hydraulic servo 30 is connected to the shaft of the planetary gear DP and the counter gear 15.
- the counter gear arranged parallel to the input shaft 12 and connected to the ring gear R3.
- the countershaft 81 connected via the gear 15 is transmitted, and the output rotation from the ring gear R3 is transmitted to the countershaft 81 via the counter gear 15. Therefore, the vehicle automatic transmission 1 is used for an FF type vehicle. Can be preferable.
- the counter gear 15 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, and is supported by the support portion 120a connected to the support wall 120 extending from the case 4.
- the counter gear 15 can be prevented from moving away from the input side force in the axial direction.
- the counter shaft portion 80 and the differential gear portion 90 can be brought closer to the torque converter 7 side, so that the vehicle automatic transmission Compact 1
- the carrier CR1 is connected to the input shaft 12 on the planetary gear unit PU side with respect to the planetary gear DP, and the second clutch C is connected to the planetary gear DP on the side opposite to the planetary gear unit PU in the axial direction.
- the hub member 112 which is the transmission member on the input side of 2
- the transmission member 112 on the input side of the carrier CR1 and the second clutch C 2 and the input shaft 12 can be connected without complicating the members.
- the hub member 116 of the first brake B-1 and the transmission member 104 connected thereto are connected to the sun gear S2 on the opposite side of the planetary gear DP in the planetary gear unit PU in the axial direction,
- the hub member 116 and the transmission member 104 of the brake B-1 can be connected to the sun gear S2 without complicating the members, and the automatic transmission 1 for the vehicle can be connected.
- the planetary gear DP supports the sun gear S1 whose rotation is always fixed with respect to the case 4, the pin-on gear P1, and the pin-on gear P2 so as to be rotatable and is always connected to the input shaft 12. Since it comprises CR1 and a ring gear R1 that meshes with the pinion gear P2 and outputs a reduced speed rotation, it is possible to output a reduced speed rotation that reduces the input rotation of the input shaft 12 from the ring gear R1.
- planetary gear unit PU has sun gear S2, sun gear S3, short pinion P3 that mates with sun gear S3, and sun gear S2 that mates with short pinion P3.
- Rabbito type planetary gear unit PU having a long pinion P4, a carrier CR2 that rotatably supports the short pinion P3 and the long pinion P4, and a ring gear R3 meshing with the long pinion P4. Therefore, each rotating element of the planetary gear unit PU and the output side member of each clutch or brake can be connected without interfering with each other, but high rotation speed of each rotating element can be prevented. A good gear ratio can be obtained.
- the first clutch C-1 is engaged and the second brake B-2 is locked to engage the first forward speed
- the first clutch C-1 is engaged and the first brake
- the second forward speed is established.
- the third forward speed is established, and the first clutch C-1 is engaged.
- the fourth clutch C-4 are engaged with the fourth forward speed, and the first clutch C-1 and the second clutch C-2 are engaged with the fifth forward speed. 6th forward speed by engaging clutch C-2 and 4th clutch C-4, 7th forward speed by engaging 2nd clutch C-2 and 3rd clutch C-3
- the forward eighth gear is engaged, and the third clutch C-3 or the fourth clutch C-4 is engaged. More reverse gear to lock the second brake B- 2, can be achieved, respectively.
- the vertical axis indicates the rotational speeds of the sun gear S2, sun gear S3, carrier CR2, and ring gear R3 of the planetary gear unit PU, and the horizontal axis indicates the gears of the sun gear S2, sun gear S3, carrier CR2, and ring gear R3.
- the sun gear S2 is positioned at the end of the lateral direction, and is configured correspondingly to the carrier CR2, the ring gear R3 connected to the counter gear 15, and the sun gear S3 in this order. Can do.
- the vehicle automatic transmission 1 according to the second embodiment is configured so that the speed change mechanism 2 is
- FIG. 6 is a cross-sectional view showing an automatic transmission 1 according to the third embodiment.
- the automatic transmission 1 according to the third embodiment is the same as the automatic transmission 1 according to the first embodiment.
- the hydraulic servo 30 of the second clutch C-2 and the hydraulic servo 20 of the first clutch C-1 are rearranged between the planetary gear DP and the planetary gear unit PU in the axial direction.
- the hydraulic servo 30 of C-2 is disposed adjacent to the support wall 120 between the counter gear 15 and the hydraulic servo 20 of the first clutch C-1, and the hydraulic servo 20 of the first clutch C-1 is It is arranged on the support wall 120 between the axial direction of the hydraulic servo 30 of the second clutch C 2 and the hydraulic servo 40 of the third clutch C 3.
- the fourth clutch C-4 is connected to the input shaft 12 and the sun gear.
- the second clutch C-2 is placed on the transmission path connecting between the carrier CR1 and the carrier CR2, and the second clutch C-2 is arranged on the transmission path connecting to the S2. Since the output-side transmission member 103 of the clutch C-2 is connected to the carrier CR2 on the planetary gear DP in the axial direction of the planetary gear unit PU, a member for enclosing the planetary gear unit PU can be eliminated. As a result, the automatic transmission 1 for the vehicle
- a support wall 120 may be provided to enable the configuration in which the hydraulic fluid for the clutch is supplied from the support wall 120, thereby reducing the number of seal rings. Can reduce the sliding resistance of the seal ring. Therefore, the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- the support wall 120 is connected to the hydraulic servo 30 of the second clutch C2.
- the oil passage provided inside can also be able to supply hydraulic oil.
- the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case where hydraulic oil is supplied.
- the power transmission efficiency as the dynamic transmission 1 can be improved.
- the friction plate 51 of the fourth clutch C 4 is relatively outer circumferential. Since the friction plate 51 can be arranged on the side and the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of friction plates can be reduced. Furthermore, it is possible to supply hydraulic oil to the hydraulic servo 50 of the fourth clutch C-4 also in an oil passage provided in the box portion 3d connected to one end of the case 4. As a result, the oil passage provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. The power transmission efficiency of the automatic transmission 1 can be improved.
- the hydraulic servo 40 of the third clutch C 3 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, the planetary gear PU is opposite to the planetary gear PU with respect to the planetary gear DP.
- the output of the third clutch C-3 which can shorten the distance between the third clutch C-3 and the planetary gear unit PU and requires strength to transmit high torque,
- the side transmission member 101 can be shortened. As a result, it is possible to achieve light weight and improve controllability as the vehicle automatic transmission 1.
- the hydraulic servo 20 of the first clutch C 1 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, the planetary gear PU is opposite to the planetary gear PU with respect to the planetary gear DP.
- the output of the first clutch C-1 which can reduce the distance between the first clutch C-1 and the planetary gear unit PU, and requires strength to transmit high torque,
- the side transmission member 102 can be shortened. This makes it light As a result, it is possible to improve the controllability of the vehicle automatic transmission 1.
- the first brake B-1 that can freely lock the rotation of the sun gear S2 with respect to the case 4 is provided, and the hydraulic servo 60 of the first brake B-1 is connected to the planetary gear unit PU with the planetary gear DP. Since it is arranged on the opposite side in the axial direction, the locking force transmission member of the first brake B-1 and the sun gear S2 can be connected without complicating the members.
- the output-side transmission member 103 is connected to the carrier CR2 through the outer peripheral side of the output-side transmission members 101, 102 of the third and first clutches C-3, C-1, and the fourth clutch C-4.
- the output-side transmission member 104 and the output-side transmission member 101 of the third clutch C-3 are connected to the sun gear S2, and the output-side transmission member 104 of the fourth clutch C4, which rotates integrally therewith, Since the transmission member 101 on the output side of the third clutch C-3 and the sun gear S2 are arranged on the inner peripheral side with respect to the transmission member 102 on the output side of the first clutch C-1, the second clutch C-2
- the transmission member 104 on the output side of the fourth clutch C-4, which rotates at a higher speed than the transmission member 103 on the output side of the first output is located on the inner peripheral side of the transmission member 103 on the output side of the second clutch C-2.
- the inner diameter side of the output member 102 on the output side of the clutch C 1 is set to the inner peripheral side. And it is a child less than the diameter of the output side of the transfer member 103 of the latch C-2, it is possible to reduce the weight I spoon than when disposed on the outer peripheral side. In addition, since inertia (inertial force) can be reduced as compared with the case where it is arranged on the outer peripheral side, the controllability of the vehicle automatic transmission 1 can be improved.
- the third and first clutches C-3, C-1 are arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the outputs of the third and first clutches C-3, C-1 Side transmission members 101 and 102 are connected to the sun gear S2 and sun gear S3, respectively, and the fourth clutch C-4 is arranged on the side opposite to the planetary gear DP in the axial direction with respect to the planetary gear unit PU.
- the transmission member 104 on the output side of C-4 is connected to the sun gear S2, and the second clutch C2 is arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the transmission member on the output side of the second clutch C-2 103, 3rd and 1st clutch C -Since it is connected to the carrier CR2 through the outer peripheral side of the transmission member 101, 102 on the output side of 3, C—l, the fourth rotation speed is higher than that of the transmission member 103 on the output side of the second clutch C-2.
- the diameter of the transmission member 104 on the output side of the fourth clutch C 4 is set to the diameter of the transmission member 103 on the output side of the second clutch C-2. It can be made smaller, and lighter weight can be achieved than when the outer peripheral side is used. In addition, the inertia (inertial force) can be reduced compared to the case of the outside, so the vehicle automatic transmission 1 and
- the friction plate 51 of the fourth clutch C-4 is arranged relatively on the outer peripheral side compared to the hydraulic servo 50 of the fourth clutch C4 arranged between the planetary gear unit PU and the planetary gear DP. Since the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of the friction plates 51 can be reduced. In addition, the distance between the third and first clutches C-3, C-1 and the planetary gear unit PU can be shortened, and the third and first clutches C-3, which are strong enough to transmit high torque, are required. , C-1 output side transmission members 101 and 102 can be shortened. As a result, a light weight can be achieved, and the controllability of the vehicle automatic transmission 1 can be improved.
- the transmission member on the input side of the fourth clutch C-4 it is connected to the input shaft 12 and the intermediate shaft 13 that pass through the inner peripheral side of the planetary gear unit PU, and the transmission on the input side of the fourth clutch C4.
- Part of the member is configured as the clutch drum 52 of the hydraulic servo 50 of the fourth clutch C—4, so that the transmission member on the output side of the fourth clutch C—4 is configured as the clutch drum of the hydraulic servo 50. Since the clutch drum of the hydraulic servo 50 can also serve as a power transmission member from the input shaft 12, it can be configured compactly in the axial direction.
- the planetary gear unit PU and the planetary gear are connected to the ring gear R3.
- a counter gear 15 disposed between the DP and the axial direction is provided.
- the counter gear 15 is connected to a support wall 120 extending from the case 4 and has a support portion 120a for supporting the counter gear 15.
- the second hub member 112 is connected to the carrier CR1 through the outer peripheral sides of the third and first clutches C-3, C-1, and a part of the transmission member 103 on the output side of the second clutch C-2 is connected to the carrier CR1.
- the second clutch C-2 is configured as a clutch drum 32 of the hydraulic servo 30 of the second clutch C-2, and the hydraulic servo 30 is disposed on the support portion 120a between the axial direction of the planetary gear DP and the counter gear 15, so that the second clutch C — It is possible to supply hydraulic oil to the hydraulic servo 30 of 2 from an oil passage c30 provided in the support portion 120a. As a result, the number of seal rings can be reduced and the sliding resistance of the seal rings can be reduced, compared with the case where, for example, the oil passage force hydraulic oil provided in the input shaft 12 is supplied. For automatic transmission 1
- the transmission member 102 on the output side of the first clutch C-1 is connected to the sun gear S3, and a part of the transmission member 102 on the output side of the first clutch C-1 is connected to the hydraulic pressure of the first clutch C-1.
- It is configured as a clutch drum 22 of the servo 20, and the hydraulic servo 20 is disposed on the support 120a between the planetary gear DP and the hydraulic servo 30 of the second clutch C-2 on the support portion 120a, and the third clutch
- the transmission member 101 on the output side of C-3 is connected to the sun gear S2, and a part of the transmission member 101 on the output side of the third clutch C-3 is connected to the clutch drum 42 of the hydraulic servo 40 of the third clutch C-3.
- the support extended from the case 4 to the hydraulic servo 20 of the first clutch C 1 is configured. Oil is supplied from the oil passage c20 provided in the wall 120 and the support 120a. It may be possible to feed. As a result, the number of seal rings can be reduced, and the sliding resistance of the seal rings can be reduced as compared with the case where the oil passage installed in the input shaft 12 supplies hydraulic oil. Automatic transmission 1
- the power transmission efficiency can be improved.
- the hydraulic servo 40 of the third clutch C 3 is arranged between the planetary gear unit PU and the planetary gear DP, for example, it is arranged on the opposite side of the planetary gear unit PU from the planetary gear unit PU in the axial direction. Compared to this, the distance between the third clutch C-3 and the planetary gear unit PU can be shortened, and transmission on the output side of the third clutch C 3 that requires strength to transmit high torque is possible.
- the member 101 can be shortened. As a result, light weight can be achieved, and controllability can be improved as a vehicle automatic transmission.
- a counter shaft 81 is provided which is arranged in parallel to the input shaft 12 and connected via the counter gear 15 connected to the ring gear R3, and the output rotation from the ring gear R3 1S via the counter gear 15 Since it is transmitted to the counter shaft 81, the vehicle automatic transmission 1 can be suitably used for an FF type vehicle.
- the counter gear 15 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, and is supported by the support portion 120a connected to the support wall 120 extending from the case 4.
- the counter gear 15 can be prevented from moving away from the input side force in the axial direction.
- the counter shaft portion 80 and the differential gear portion 90 can be brought closer to the torque converter 7 side, so that the vehicle automatic transmission Compact 1
- the carrier CR1 is connected to the input shaft 12 on the planetary gear unit PU side with respect to the planetary gear DP, and the second clutch C is connected to the planetary gear DP on the side opposite to the planetary gear unit PU in the axial direction.
- 2 is connected to the hub member 112, which is the transmission member on the input side, so that the transmission member 112 on the input side of the carrier CR1 and the second clutch C2 and the input shaft 12 can be connected without complicating the members.
- the hub member 116 of the first brake B-1 and the transmission member 104 connected thereto are connected to the sun gear S2 on the opposite side in the axial direction from the planetary gear DP in the planetary gear unit PU,
- the hub member 116 and the transmission member 104 of the brake B-1 can be connected to the sun gear S2 without complicating the members, and the automatic transmission 1 for the vehicle can be connected.
- the planetary gear DP is a carrier that supports the sun gear S1 whose rotation is always fixed with respect to the case 4, the pin-on gear P1, and the pin-on gear P2 rotatably and is always connected to the input shaft 12.
- CR1 and ring gear R1 that meshes with the pinion gear P2 and outputs the reduced speed rotation. It is possible to output from Rl.
- the planetary gear unit PU includes a sun gear S2, a sun gear S3, a short pinion P3 that meshes with the sun gear S3, a long pinion P4 that meshes with the sun gear S2, and meshes with the short peer P3, Since each of the planetary gear units PU is comprised of a radio gear type planetary gear unit PU having a carrier CR2 that rotatably supports the short pinion P3 and the long pinion P4 and a ring gear R3 that meshes with the long pinion P4. While it is possible to connect the rotating element and the output side member of each clutch or brake without complicating the members, the high rotating speed of each rotating element can be prevented and a good gear ratio can be obtained. be able to.
- the first clutch C-1 is engaged and the second brake B-2 is locked to engage the first forward speed
- the first clutch C-1 is engaged and the first brake
- the second forward speed is established.
- the third forward speed is established, and the first clutch C-1 is engaged.
- the fourth clutch C-4 are engaged with the fourth forward speed, and the first clutch C-1 and the second clutch C-2 are engaged with the fifth forward speed. 6th forward speed by engaging clutch C-2 and 4th clutch C-4, 7th forward speed by engaging 2nd clutch C-2 and 3rd clutch C-3
- the forward eighth gear is engaged, and the third clutch C-3 or the fourth clutch C-4 is engaged. More reverse gear to lock the second brake B- 2, can be achieved, respectively.
- the vertical axis indicates the rotation speed of sun gear S2, sun gear S3, carrier CR2, and ring gear R3 of planetary gear unit PU
- the horizontal axis indicates the gears of sun gear S2, sun gear S3, carrier CR2, and ring gear R3.
- the sun gear S2 is positioned at the end of the lateral direction, and is configured correspondingly to the carrier CR2, the ring gear R3 connected to the counter gear 15, and the sun gear S3 in this order. Can do.
- vehicle automatic transmission 1 according to the third embodiment has the transmission mechanism 2 in the left-right direction.
- FIG. 7 is a sectional view showing an automatic transmission 1 according to the fourth embodiment.
- the automatic transmission 1 according to the fourth embodiment is the same as the automatic transmission 1 according to the first embodiment.
- the hydraulic servo 30 of the second clutch C-2 and the hydraulic servo 20 of the first clutch C-1 are repositioned between the planetary gear DP and the planetary gear unit PU in the axial direction of the third clutch C.
- the third hydraulic servo 40 is configured by changing the arrangement of the planetary gear DP on the opposite side of the planetary gear unit PU in the axial direction.
- the hydraulic servo 30 of the second clutch C 2 is disposed adjacent to the support wall 120 in the axial direction between the counter gear 15 and the hydraulic servo 20 of the first clutch C—1, and the first clutch C—1
- the hydraulic servo 20 is disposed on the support wall 120 between the hydraulic servo 30 of the second clutch C 2 and the planetary gear DP
- the hydraulic servo 40 of the third clutch C-3 is disposed on the boss 3b. It is composed.
- the hydraulic servo 40 of the third clutch C 3 is connected to the planetary gear.
- the planetary gear unit PU is disposed on the opposite side of the planetary gear unit PU with respect to the DP.
- the hydraulic servo 20 of the first clutch C—1, the hydraulic servo 30 of the second clutch C—2, and the counter gear 15 are connected to the planetary gear DP and the planetary gear.
- the hydraulic servo 50 of the fourth clutch C 4 and the hydraulic servo 60 of the first brake B—1 are arranged on the opposite side of the planetary gear DP with respect to the planetary gear unit PU. Has been.
- the fourth clutch C-4 is connected to the input shaft 12 and the sun gear.
- the second clutch C-2 is placed on the transmission path connecting between the carrier CR1 and the carrier CR2, and the second clutch C-2 is arranged on the transmission path connecting to the S2. Since the output transmission member 103 of the clutch C-2 is connected to the carrier CR2 on the planetary gear DP side in the axial direction of the planetary gear unit PU, a member for enclosing the planetary gear unit PU can be eliminated. As a result, the automatic transmission 1 for the vehicle
- a support wall 120 can be provided to enable the configuration in which the hydraulic fluid for the clutch is supplied from the support wall 120, thereby reducing the number of seal rings. Therefore, the sliding resistance of the seal ring can be reduced, and the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- the support wall 120 is connected to the hydraulic servo 30 of the second clutch C2.
- the oil passage provided inside can also be able to supply hydraulic oil.
- the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case where hydraulic oil is supplied.
- the power transmission efficiency as the dynamic transmission 1 can be improved.
- the friction plate 51 of the fourth clutch C 4 is relatively outer circumferential. Since the friction plate 51 can be arranged on the side and the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of friction plates can be reduced. Furthermore, it is possible to supply hydraulic oil to the hydraulic servo 50 of the fourth clutch C-4 also in an oil passage provided in the box portion 3d connected to one end of the case 4. As a result, the oil passage provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. The power transmission efficiency of the automatic transmission 1 can be improved.
- the hydraulic servo 40 of the third clutch C 3 is arranged on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, one end of the case 4 is connected to the hydraulic servo 40 of the third clutch C-3. It is possible to supply the oil passage force hydraulic oil provided in the boss portion 3b connected to the boss portion 3b. As a result, the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. Improve power transmission efficiency as an automatic transmission 1 Togashi.
- the hydraulic servo 20 of the first clutch C 1 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, the planetary gear PU is opposite to the planetary gear PU with respect to the planetary gear DP.
- the output of the first clutch C-1 which can reduce the distance between the first clutch C-1 and the planetary gear unit PU, and requires strength to transmit high torque,
- the side transmission member 102 can be shortened. As a result, it is possible to achieve light weight and improve controllability as the vehicle automatic transmission 1.
- the first brake B-1 that can lock the rotation of the sun gear S2 with respect to the case 4 is provided, and the hydraulic servo 60 of the first brake B-1 is connected to the planetary gear unit PU with the planetary gear DP. Since it is arranged on the opposite side in the axial direction, the locking force transmission member of the first brake B-1 and the sun gear S2 can be connected without complicating the members.
- the output-side transmission member 103 is connected to the carrier CR2 through the outer peripheral side of the output-side transmission members 101, 102 of the third and first clutches C-3, C-1, and the fourth clutch C-4.
- the output-side transmission member 104 and the output-side transmission member 101 of the third clutch C-3 are connected to the sun gear S2, and the output-side transmission member 104 of the fourth clutch C4, which rotates integrally therewith, Since the transmission member 101 on the output side of the third clutch C-3 and the sun gear S2 are arranged on the inner peripheral side with respect to the transmission member 102 on the output side of the first clutch C-1, the second clutch C-2
- the transmission member 104 on the output side of the fourth clutch C-4, which rotates at a higher speed than the transmission member 103 on the output side of the first output is located on the inner peripheral side of the transmission member 103 on the output side of the second clutch C-2.
- the inner diameter side of the output member 102 on the output side of the clutch C 1 is set to the inner peripheral side. And it is a child less than the diameter of the output side of the transfer member 103 of the latch C-2, it is possible to reduce the weight I spoon than when disposed on the outer peripheral side. In addition, since inertia (inertial force) can be reduced as compared with the case where it is arranged on the outer peripheral side, the controllability of the vehicle automatic transmission 1 can be improved.
- the third and first clutches C-3 and C-1 are connected to the planetary gear unit PU.
- the transmission members 101 and 102 on the output side of the third and first clutches C-3 and C-1 are connected to the sun gear S2 and sun gear S3, respectively, and the fourth clutch C-4 is connected.
- the planetary gear unit PU is disposed on the opposite side of the planetary gear DP in the axial direction, the transmission member 104 on the output side of the fourth clutch C-4 is connected to the sun gear S2, and the second clutch C2 is connected to the planetary gear unit PU.
- the transmission member 103 on the output side of the second clutch C-2 is connected to the outer periphery of the transmission members 101 and 102 on the output side of the third and first clutches C-3 and C-1. Because the transmission member 104 on the output side of the fourth clutch C4, which rotates faster than the transmission member 103 on the output side of the second clutch C-2, is on the inner peripheral side. 4th clutch C 4 output side transmission member 104 of And it can be smaller than the diameter of the second clutch C-2 on the output side of the transmission member 103, it is possible to reduce the weight I spoon than when the outer peripheral side. In addition, the inertia (inertial force) can be reduced compared to the case of the outside, so the vehicle automatic transmission 1 and
- the friction plate 51 of the fourth clutch C-4 is arranged relatively on the outer peripheral side compared to the hydraulic servo 50 of the fourth clutch C4 arranged between the planetary gear unit PU and the planetary gear DP. Since the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of the friction plates 51 can be reduced. In addition, the distance between the third and first clutches C-3, C-1 and the planetary gear unit PU can be shortened, and the third and first clutches C-3, which are strong enough to transmit high torque, are required. , C-1 output side transmission members 101 and 102 can be shortened. As a result, a light weight can be achieved, and the controllability of the vehicle automatic transmission 1 can be improved.
- the transmission member on the input side of the fourth clutch C-4 it is connected to the input shaft 12 and the intermediate shaft 13 that pass through the inner peripheral side of the planetary gear unit PU, and the input side of the fourth clutch C4.
- Part of the transmission member is configured as the clutch drum 52 of the hydraulic clutch 50 of the fourth clutch C—4. Therefore, the transmission member on the output side of the fourth clutch C—4 is configured as the clutch drum of the hydraulic servo 50.
- the clutch drum of the hydraulic servo 50 can also serve as a power transmission member from the input shaft 12, so that it can be made compact in the axial direction.
- the counter gear 15 is connected to the ring gear R3 and is arranged between the planetary gear unit PU and the planetary gear DP in the axial direction.
- the counter gear 15 is connected to the support wall 120 extending from the case 4, and the counter gear. 15 and supporting the hub member 112 of the second clutch C-2 through the outer peripheral side of the third and first clutches C-3, C-1, and to the carrier CR1,
- a part of the transmission member 103 on the output side of the second clutch C-2 is configured as a clutch drum 32 of the hydraulic servo 30 of the second clutch C-2, and the hydraulic servo 30 is connected to the shaft of the planetary gear DP and the counter gear 15.
- a part of the member is configured as a clutch drum 22 of the hydraulic servo 20 of the first clutch C—1, and the hydraulic servo 20 is arranged between the planetary gear DP and the hydraulic servo 30 of the second clutch C 2 in the axial direction. Since it is placed on the support 120a, the hydraulic pressure of the third clutch C
- the turbo 40 it is possible to be able to supply feed the working oil from the oil passage c40 provided in the boss portion 3b that is linked to the side wall 3a of the case 4.
- the hydraulic support of the third clutch C 3 Compared to the case where the robot 40 is disposed on the input shaft 12 away from the boss 3b and hydraulic oil is supplied through the oil passage in the input shaft 12, the oil passage in the input shaft 12 is not interposed.
- the oil path length can be shortened and the controllability of the vehicle automatic transmission 1 can be improved.
- the oil passage provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil.
- the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- the counter shaft 81 is arranged in parallel to the input shaft 12 and connected via the counter gear 15 connected to the ring gear R3, and the output rotation from the ring gear R3 1S via the counter gear 15 Since it is transmitted to the counter shaft 81, the vehicle automatic transmission 1 can be suitably used for an FF type vehicle.
- the counter gear 15 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, and is supported by the support portion 120a connected to the support wall 120 extending from the case 4,
- the counter gear 15 can be prevented from moving away from the input side force in the axial direction.
- the counter shaft portion 80 and the differential gear portion 90 can be brought closer to the torque converter 7 side, so that the vehicle automatic transmission Compact 1
- the carrier CR1 is connected to the input shaft 12 on the planetary gear unit PU side with respect to the planetary gear DP, and the second clutch C is connected to the planetary gear DP on the side opposite to the planetary gear unit PU in the axial direction.
- 2 is connected to the hub member 112, which is the transmission member on the input side, so that the transmission member 112 on the input side of the carrier CR1 and the second clutch C2 and the input shaft 12 can be connected without complicating the members.
- hub member 116 of the first brake B-1 and the transmission member 104 connected thereto are connected to the sun gear S2 on the side opposite to the planetary gear DP in the planetary gear unit PU, Hub member 116 and transmission member 104 of brake B-1 Gear S2 can be connected without complicating parts, and the vehicle automatic transmission 1 can be connected.
- planetary gear DP supports a sun gear S1 whose rotation is always fixed with respect to case 4, pinion gear P1 and pinion gear P2, and a carrier that is always connected to input shaft 12. Since it comprises CR1 and a ring gear R1 that meshes with the pinion gear P2 and outputs a reduced speed rotation, it is possible to output a reduced speed rotation that reduces the input rotation of the input shaft 12 from the ring gear R1.
- the planetary gear unit PU includes a sun gear S2, a sun gear S3, a short pinion P3 that meshes with the sun gear S3, and a long pinion P4 that meshes with the sun gear S2 and meshes with the short peer P3, Since each of the planetary gear units PU is comprised of a radio gear type planetary gear unit PU having a carrier CR2 that rotatably supports the short pinion P3 and the long pinion P4 and a ring gear R3 that meshes with the long pinion P4. While it is possible to connect the rotating element and the output side member of each clutch or brake without complicating the members, the high rotating speed of each rotating element can be prevented and a good gear ratio can be obtained. be able to.
- the first clutch C-1 is engaged and the second brake B-2 is locked to engage the first forward speed
- the first clutch C-1 is engaged and the first brake
- the second forward speed is established.
- the third forward speed is established, and the first clutch C-1 is engaged.
- the fourth clutch C-4 are engaged with the fourth forward speed, and the first clutch C-1 and the second clutch C-2 are engaged with the fifth forward speed. 6th forward speed by engaging clutch C-2 and 4th clutch C-4, 7th forward speed by engaging 2nd clutch C-2 and 3rd clutch C-3
- the forward eighth gear is engaged, and the third clutch C-3 or the fourth clutch C-4 is engaged. More reverse gear to lock the second brake B- 2, can be achieved, respectively.
- sun gear S2 can be configured to correspond to the ring gear R3 and the sun gear S3, which are positioned at the end in the lateral direction and sequentially connected to the carrier CR2 and the counter gear 15.
- vehicle automatic transmission 1 according to the present fourth embodiment has the transmission mechanism 2 in the left-right direction.
- the vehicle automatic transmission 1 By reversing substantially in the axial direction, the vehicle automatic transmission 1 according to a ninth embodiment to be described later can be configured.
- FIG. 8 is a sectional view showing an automatic transmission 1 according to the fifth embodiment.
- FIG. 9 is a skeleton diagram showing an automatic transmission 1 according to the fifth embodiment.
- the automatic transmission 1 according to the fifth embodiment is the same as the automatic transmission 1 according to the first embodiment.
- the hydraulic servo 40 of the third clutch C 3 is rearranged in the axial direction opposite to the planetary gear unit PU with respect to the planetary gear DP.
- the hydraulic servo 30 of the second clutch C-2 is disposed adjacent to the support wall 120 in the axial direction between the counter gear 15 and the hydraulic servo 20 of the first clutch C-1 so that the first clutch C1
- the hydraulic servo 20 is disposed on the support wall 120 between the hydraulic servo 30 of the second clutch C 2 and the hydraulic servo 50 of the fourth clutch C 4, and the hydraulic servo 50 of the fourth clutch C-4 is installed.
- the fourth gear C—4 hydraulic servo 50, the first clutch C—1 hydraulic servo 20 and the second clutch C—2 hydraulic servo are arranged on the opposite side of the planetary gear unit PU with respect to the DP.
- 30 and counter gear 15 are connected to planetary gear DP and planetary gear unit PU.
- the hydraulic servo 60 of the first brake B-1 is arranged between the axial directions, and is arranged on the opposite side of the planetary gear DP with respect to the planetary gear unit PU.
- the fourth clutch C-4 can be disposed on the input shaft 12, so that it is not necessary to always transmit the input rotation to the intermediate shaft 13. Therefore, the input shaft 12 and the intermediate shaft 13 can be separated so as to be rotatable relative to each other, and the intermediate shaft 13 can be used as a so-called intermediate shaft, and the intermediate shaft 13 can be used as the third clutch C— 3 can be used as a power transmission member that transmits the deceleration rotation from 3 and the input rotation from the fourth clutch C-4, that is, the intermediate shaft 13 is the output transmission member of the third clutch C-3. 101 and the output clutch 104 of the fourth clutch C-4 can be shared. Thus, sliding resistance can be reduced as compared with the case where the transmission member 101 is covered on the intermediate shaft 13, and transmission efficiency as the vehicle automatic transmission 1 can be improved.
- the second brake B-2 is locked to the case 4 by tightening the clutch drum 32 of the second clutch C-2 with the brake band 171.
- It is composed of a so-called band brake and is equipped with a one-wichi clutch F-1 that regulates the rotation of the planetary gear unit PU in one direction of the carrier CR2.
- the first clutch C-1 and the one-way clutch F-1 force S are engaged.
- the rotational force of the ring gear R1 decelerated by the fixed sun gear S1 and the input rotation carrier CR1 is input to the sun gear S3 via the first clutch C-1.
- the rotation of the carrier CR2 is restricted to one direction (forward rotation direction), that is, the reverse rotation of the carrier CR2 is prevented and fixed.
- the decelerated rotation input to the sun gear S3 is output to the ring gear R3 via the fixed carrier CR2, and the forward rotation as the first forward speed is output from the counter gear 15.
- the second brake B-2 is locked and the carrier CR2 is fixed to prevent forward rotation of the carrier CR2. Maintain the state of. At the first forward speed, the one-way clutch F-1 prevents reverse rotation of the carrier CR2 and enables forward rotation. Achievement of the first forward speed when switching to the range can be achieved smoothly by automatic engagement of the one-way clutch F-1.
- the fourth clutch C-4 is connected to the input shaft 12 and the sun gear.
- the second clutch C-2 is placed on the transmission path connecting between the carrier CR1 and the carrier CR2, and the second clutch C-2 is arranged on the transmission path connecting to the S2. Since the output transmission member 103 of the clutch C-2 is connected to the carrier CR2 on the planetary gear DP side in the axial direction of the planetary gear unit PU, a member for enclosing the planetary gear unit PU can be eliminated. As a result, the automatic transmission 1 for the vehicle
- a support wall 120 can be provided to enable the configuration in which the hydraulic fluid for the clutch is supplied from the support wall 120, thereby reducing the number of seal rings. Therefore, the sliding resistance of the seal ring can be reduced, and the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- the support wall 120 is connected to the hydraulic servo 30 of the second clutch C2.
- the oil passage provided inside can also be able to supply hydraulic oil.
- the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case where hydraulic oil is supplied.
- the power transmission efficiency as the dynamic transmission 1 can be improved.
- the hydraulic servo 50 of the fourth clutch C 4 is disposed adjacent to the planetary gear DP between the planetary gear unit PU and the planetary gear DP in the axial direction, the carrier CR1 and the fourth clutch C-4 Part of the components that make up the clutch drum 52 of the hydraulic servo 50 (that is, the clutch drum 52 and the side plate of the carrier CR1) can be shared. The amount can be improved.
- the hydraulic servo 40 of the third clutch C-3 is arranged on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, the hydraulic servo 40 of the third clutch C-3 is connected to the hydraulic servo 40 of the case 4. It is possible to supply oil passage force hydraulic oil provided in the boss 3b connected to one end. As a result, the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. To improve power transmission efficiency as an automatic transmission 1
- the hydraulic servo 20 of the first clutch C 1 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, the hydraulic servo 20 of the first clutch C 1 is placed in the support wall 120. It is possible to supply the hydraulic oil to the oil passage provided in the oil passage. As a result, the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case where hydraulic oil is supplied. The power transmission efficiency as the dynamic transmission 1 can be improved.
- the first brake B-1 that can freely lock the rotation of the sun gear S2 with respect to the case 4 is provided, and the hydraulic servo 60 of the first brake B-1 is connected to the planetary gear unit PU with the planetary gear DP. Since it is arranged on the opposite side in the axial direction, the locking force transmission member of the first brake B-1 and the sun gear S2 can be connected without complicating the members.
- the output-side transmission member 103 is connected to the carrier CR2 through the outer peripheral side of the output-side transmission members 101, 102 of the third and first clutches C-3, C-1, and the fourth clutch C-4.
- the output shaft of the intermediate shaft 13 and the output clutch 101 of the output of the third clutch C-3 are connected to the sun gear S2 and the output of the fourth clutch C-4 that rotates integrally therewith.
- the intermediate shaft 13, which is the transmission member on the side, the transmission member 101 on the output side of the third clutch C-3, and the sun gear S2 are located on the inner peripheral side with respect to the transmission member 102 on the output side of the first clutch C-1.
- the intermediate shaft 13 serving as the transmission member on the output side of the fourth clutch C-4, which rotates faster than the transmission member 103 on the output side of the second clutch C-2, is connected to the output of the second clutch C2.
- Side transmission member 1 03, the inner shaft 13 is located on the inner peripheral side of the output member 102 on the output side of the first clutch C-1 on the inner peripheral side of the third clutch C-1.
- the diameter of the transmission member 103 on the output side of the clutch C-2 can be made smaller, and a lighter weight can be achieved than when it is arranged on the outer peripheral side.
- the inertia inertia force
- the third and first clutches C-3, C-1 are arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the outputs of the third and first clutches C-3, C-1 are provided.
- Side transmission members 101 and 102 are connected to the sun gear S2 and sun gear S3, respectively, and the fourth clutch C-4 is arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the output side of the fourth clutch C-4
- the intermediate shaft 13 which is the transmission member of the second clutch C2 is connected to the sun gear S2, the second clutch C2 is disposed on the planetary gear DP side with respect to the planetary gear unit PU, and the transmission member 103 on the output side of the second clutch C-2 is provided.
- the output side transmission member 103 of the second clutch C-2 is connected. 4th clutch C— Since the intermediate shaft 13 that is the output member of the output side 4 is the inner peripheral side, the diameter of the intermediate shaft 13 that is the output member of the fourth clutch C 4 is set to the The diameter of the transmission member 103 can be made smaller than that of the transmission member 103, and the weight can be reduced compared to the case of the outer peripheral side. In addition, since inertia (inertia force) can be reduced as compared with the case of the outer peripheral side, the controllability of the vehicle automatic transmission 1 can be improved.
- the transmission member on the input side of the fourth clutch C-4 it is directly connected to the carrier CR1, and is configured as a part of the hydraulic servo 50 of the fourth clutch C-4 with a part of the carrier CR1.
- Part of the components that make up the carrier CR1 and the hydraulic servo 50 of the fourth clutch C-4 can be shared. You can make a habit.
- the counter gear 15 is connected to the ring gear R3 and disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, and is connected to the support wall 120 extending from the case 4 and is also connected to the counter gear. 15 has a support part 120a for supporting
- the hub member 112 of the latch C-2 is connected to the carrier CR1 through the outer peripheral side of the third and first clutches C-3, C-1, and the transmission member 103 of the output side of the second clutch C-2 is connected to the carrier CR1.
- a part is configured as the clutch drum 32 of the hydraulic servo 30 of the second clutch C-2, and the hydraulic servo 30 is disposed on the support 120a between the axial direction of the planetary gear DP and the counter gear 15, so that the first It is possible to supply hydraulic oil to the hydraulic servo 30 of the two-clutch C-2 also with the oil passage c30 provided in the support portion 120a.
- the number of seal rings can be reduced and the sliding resistance of the seal rings can be reduced, compared with the case where, for example, the oil passage force hydraulic oil provided in the input shaft 12 is supplied.
- the power transmission efficiency can be improved.
- the hydraulic servo 40 of the third clutch C 3 is disposed on the input shaft 12 away from the boss portion 3b, and hydraulic oil is supplied through the oil passage in the input shaft 12. Therefore, the oil passage length can be shortened by the amount that the oil passage in the input shaft 12 is not interposed, and the controllability of the vehicle automatic transmission 1 can be improved.
- the vehicle automatic transmission 1 can be suitably used for an FF type vehicle.
- the counter gear 15 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, and is supported by the support portion 120a connected to the support wall 120 extending from the case 4.
- the counter gear 15 can be prevented from moving away from the input side force in the axial direction.
- the counter shaft portion 80 and the differential gear portion 90 can be brought closer to the torque converter 7 side, so that the vehicle automatic transmission Compact 1
- the carrier CR1 is connected to the input shaft 12 on the planetary gear unit PU side with respect to the planetary gear DP, and the second clutch C is connected to the planetary gear DP on the side opposite to the planetary gear unit PU in the axial direction.
- the hub member 112 which is the transmission member on the input side of 2
- the transmission member 112 on the input side of the carrier CR1 and the second clutch C 2 and the input shaft 12 can be connected without complicating the members.
- the hub member 116 of the first brake B-1 and the transmission member 104 connected thereto are connected to the sun gear S2 on the opposite side of the planetary gear DP in the planetary gear unit PU to the sun gear S2.
- the hub member 116 and the transmission member 104 of the brake B-1 can be connected to the sun gear S2 without complicating the members, and the automatic transmission 1 for the vehicle can be connected.
- the planetary gear DP is a carrier that supports the sun gear S1 whose rotation is always fixed with respect to the case 4, and the pin-on gear P1 and the pin-on gear P2 so as to be rotatable and is always connected to the input shaft 12. Since it comprises CR1 and a ring gear R1 that meshes with the pinion gear P2 and outputs a reduced speed rotation, it is possible to output a reduced speed rotation that reduces the input rotation of the input shaft 12 from the ring gear R1.
- the planetary gear unit PU is connected to the sun gear S2, the sun gear S3, and the sun gear S3.
- Short pinion P3, long pinion P4 mated to sun gear S2 and mated to short pinion P3, carrier CR2 that rotatably supports short pinion P3 and long pinion P4, and long pin -Since it is composed of a Rabiyo-type planetary gear unit PU having a ring gear R3 that meshes with P4, the rotating elements of the planetary gear unit PU and the output side members of the clutches and brakes must be connected without complications. However, it is possible to prevent the high rotation speed of each rotating element and to obtain a good gear ratio.
- the first clutch C-1 is engaged and the second brake B-2 is locked to engage the first forward speed
- the first clutch C-1 is engaged and the first brake
- the second forward speed is established.
- the third forward speed is established, and the first clutch C-1 is engaged.
- the fourth clutch C-4 are engaged with the fourth forward speed, and the first clutch C-1 and the second clutch C-2 are engaged with the fifth forward speed. 6th forward speed by engaging clutch C-2 and 4th clutch C-4, 7th forward speed by engaging 2nd clutch C-2 and 3rd clutch C-3
- the forward eighth gear is engaged, and the third clutch C-3 or the fourth clutch C-4 is engaged. More reverse gear to lock the second brake B- 2, can be achieved, respectively.
- the vertical axis indicates the rotational speed of each of the sun gear S2, sun gear S3, carrier CR2, and ring gear R3 of the planetary gear unit PU
- the horizontal axis indicates the gears of the sun gear S2, sun gear S3, carrier CR2, and ring gear R3.
- the sun gear S2 is positioned at the end of the lateral direction, and is configured correspondingly to the carrier CR2, the ring gear R3 connected to the counter gear 15, and the sun gear S3 in this order. Can do.
- vehicle automatic transmission 1 according to the fifth embodiment has the transmission mechanism 2 in the left-right direction.
- the inner peripheral side of the planetary gear unit PU is
- FIG. 11 is a cross-sectional view showing an automatic transmission 1 according to the sixth embodiment.
- the automatic transmission 1 according to the sixth embodiment is the same as the automatic transmission 1 according to the first embodiment.
- the first to fourth clutches C1 to C4 the first and second brakes B-1 to B-2, planetary gear DP, planetary gear unit PU, counter gear 15 and the like are arranged so as to be substantially reversed in the left-right direction (axial direction), that is, the speed change mechanism 2 is substantially left-right direction (axial direction).
- the transmission mechanism 2 is configured by being reversed.
- the hydraulic servo 20 of C 1 is arranged on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, and the hydraulic servo 40 of the third clutch C 3 and the counter gear 15 are connected to the planetary gear DP and the planetary gear unit PU.
- the hydraulic servo 50 of the fourth clutch C 4 and the hydraulic servo 60 of the first brake B—1 are arranged on the opposite side of the planetary gear DP with respect to the planetary gear unit PU. .
- the fourth clutch C-4 is connected to the input shaft 12 and the sun gear.
- the second clutch C-2 is placed on the transmission path connecting between the carrier CR1 and the carrier CR2, and the second clutch C-2 is arranged on the transmission path connecting to the S2. Since the output transmission member 103 of the clutch C-2 is connected to the carrier CR2 on the planetary gear DP side in the axial direction of the planetary gear unit PU, a member for enclosing the planetary gear unit PU can be eliminated. This is an automatic transmission for vehicles 1
- a support wall 120 may be provided to enable the configuration in which the hydraulic fluid for the clutch is supplied from the support wall 120, thereby reducing the number of seal rings. As a result, the sliding resistance of the seal ring can be reduced, and the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- the counter gear 15 connected to the ring gear R3 is provided, and the counter gear 15 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, and the output side member of the third clutch C-3.
- the output-side transmission member 102 of the first clutch C-1 and the output-side transmission member 103 of the second clutch C-2 are connected to the planetary gear PU through the inner peripheral side of the counter gear 15. Therefore, it is possible to dispose the counter gear 15 between the planetary gear unit PU and the planetary gear DP in the axial direction.
- the hydraulic servo 30 of the second clutch C-2 is arranged on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, the hydraulic servo 30 of the second clutch C-2 is connected to the hydraulic servo 30 of the case 4. It is possible to supply hydraulic oil from an oil passage c30 provided in the boss 3b connected to one end. As a result, the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. Improved power transmission efficiency as transmission 1
- the friction plate 51 of the fourth clutch C 4 is relatively on the outer peripheral side. Since the area of the friction plates 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of friction plates 51 can be reduced. Furthermore, hydraulic oil can be supplied to the hydraulic servo 50 of the fourth clutch C-4 from an oil passage c50 provided in the boss portion 3d connected to one end of the case 4. As a result, the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal ring as compared with the case of supplying hydraulic oil. The power transmission efficiency of the transmission 1 can be improved.
- the hydraulic servo 40 of the third clutch C 3 is connected to the planetary gear unit PU and the planetary gear. Since it is located between the shaft DP and the planetary gear DP, the third clutch C-3 and the planetary gear unit PU The output-side transmission member 101 of the third clutch C-3, which requires strength to transmit high torque, can be shortened. As a result, a light weight can be achieved and controllability can be improved as the vehicle automatic transmission 1.
- the hydraulic servo 20 of the first clutch C-1 is arranged on the opposite side of the planetary gear unit PU in the axial direction with respect to the planetary gear DP, the hydraulic servo 20 of the first clutch C-1 is connected to the hydraulic servo 20 of the case 4. It is possible to supply hydraulic oil from an oil passage c20 provided in the boss portion 3b connected to one end. As a result, for example, the hydraulic path 20 can be shortened compared to the case where the hydraulic servo 20 of the first clutch C-1 is disposed on the input shaft 12 and hydraulic oil is supplied via the input shaft 12.
- an automatic transmission for vehicles 1 is arranged on the opposite side of the planetary gear unit PU in the axial direction with respect to the planetary gear DP, the hydraulic servo 20 of the first clutch C-1 is connected to the hydraulic servo 20 of the case 4. It is possible to supply hydraulic oil from an oil passage c20 provided in the boss portion 3b connected to one end. As a result, for example, the hydraulic path 20 can be shortened compared to the
- the first brake B-1 that can lock the rotation of the sun gear S2 with respect to the case 4 is provided, and the hydraulic servo 60 of the first brake B-1 is connected to the planetary gear unit PU with the planetary gear DP. Since it is arranged on the opposite side in the axial direction, the locking force transmission member of the first brake B-1 and the sun gear S2 can be connected without complicating the members.
- the output-side transmission member 103 is connected to the carrier CR2 through the outer peripheral side of the output-side transmission members 101, 102 of the third and first clutches C-3, C-1, and the fourth clutch C-4.
- the output-side transmission member 104 and the output-side transmission member 101 of the third clutch C-3 are connected to the sun gear S2, and the output-side transmission member 104 of the fourth clutch C4, which rotates integrally therewith, Since the transmission member 101 on the output side of the third clutch C-3 and the sun gear S2 are arranged on the inner peripheral side with respect to the transmission member 102 on the output side of the first clutch C-1, the second clutch C-2
- the transmission member 104 on the output side of the fourth clutch C-4, which rotates at a higher speed than the transmission member 103 on the output side of the first output is located on the inner peripheral side of the transmission member 103 on the output side of the second clutch C-2.
- the diameter of the member 104 can be made smaller than the diameter of the transmission member 103 on the output side of the second clutch C-2, and a lighter weight can be achieved than when the member 104 is disposed on the outer peripheral side.
- inertia inertial force
- the controllability of the vehicle automatic transmission 1 can be improved.
- the third and first clutches C-3, C-1 are arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the outputs of the third and first clutches C-3, C-1 are provided.
- Side transmission members 101 and 102 are connected to the sun gear S2 and sun gear S3, respectively, and the fourth clutch C-4 is arranged on the side opposite to the planetary gear DP in the axial direction with respect to the planetary gear unit PU.
- the transmission member 104 on the output side of C-4 is connected to the sun gear S2, and the second clutch C2 is arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the transmission member on the output side of the second clutch C-2 103 is connected to the carrier CR2 through the outer peripheral sides of the output members 101, 102 on the output side of the third and first clutches C-3, C-1, so that the output on the output side of the second clutch C-2 is transmitted.
- 4th clutch C with higher rotation than member 103 Since the output member 104 on the output side 4 is the inner peripheral side, the diameter of the output member 104 on the output side of the fourth clutch C 4 is larger than the diameter of the output member 103 on the output side of the second clutch C-2. It can be made smaller and lighter than the outer peripheral side.
- the inertia inertial force
- the friction plate 51 of the fourth clutch C-4 is arranged relatively on the outer peripheral side compared to the hydraulic servo 50 of the fourth clutch C4 arranged between the planetary gear unit PU and the planetary gear DP. Since the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of the friction plates 51 can be reduced. In addition, the distance between the third and first clutches C-3, C-1 and the planetary gear unit PU can be shortened, and the third and first clutches C-3, which are strong enough to transmit high torque, are required. , C-1 output side transmission members 101 and 102 can be shortened. As a result, a light weight can be achieved, and the controllability of the vehicle automatic transmission 1 can be improved.
- hydraulic oil can be supplied to the hydraulic servo 50 of the fourth clutch C-4 from, for example, an oil passage c50 provided in the boss portion 3b connected to the side wall 3a of the case 4. .
- the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal ring as compared with the case where hydraulic fluid is supplied, so that the vehicle automatic The power transmission efficiency of the transmission 1 can be improved.
- the transmission member on the input side of the fourth clutch C-4 it is connected to the input shaft 12 and the intermediate shaft 13 that pass through the inner peripheral side of the planetary gear unit PU, and the transmission on the input side of the fourth clutch C4.
- Part of the member is configured as the clutch drum 52 of the hydraulic servo 50 of the fourth clutch C—4, so that the transmission member on the output side of the fourth clutch C—4 is configured as the clutch drum of the hydraulic servo 50. Since the clutch drum of the hydraulic servo 50 can also serve as a power transmission member from the input shaft 12, it can be configured compactly in the axial direction.
- the hydraulic servo 30 of the second clutch C-2 is disposed on the input shaft 12 away from the boss portion 3b and hydraulic oil is supplied through the oil passage in the input shaft 12.
- the oil path length can be shortened by the amount that the oil path in the input shaft 12 is not interposed, so that the controllability of the vehicle automatic transmission 1 can be improved.
- the hub member 111 of the first clutch C-1 is connected to the ring gear R1
- the output transmission member 102 of the first clutch C-1 is connected to the sun gear S3
- the first clutch C- A part of the output member 102 on the output side of 1 is configured as a clutch drum 22 of the hydraulic servo 20 of the first clutch C—1
- the hydraulic servo 20 is composed of the planetary gear DP and the hydraulic servo 20 of the second clutch C—1.
- the hydraulic servo 20 of the first clutch C-1 is disposed on the input shaft 12 away from the boss portion 3b, and the input shaft 12 Compared to the case where hydraulic fluid is supplied via the oil passage, the oil passage length can be shortened by not interposing the oil passage in the input shaft 12, and the controllability as an automatic transmission 1 for vehicles is improved.
- the counter shaft 81 is arranged in parallel to the input shaft 12 and connected via the counter gear 15 connected to the ring gear R3.
- the counter gear 15 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, and is supported by the support portion 120a connected to the support wall 120 extending from the case 4.
- the counter gear 15 can be prevented from moving away from the input side force in the axial direction.
- the counter shaft portion 80 and the differential gear portion 90 can be brought closer to the torque converter 7 side, so that the vehicle automatic transmission Compact 1
- the carrier CR1 is connected to the input shaft 12 on the planetary gear unit PU side with respect to the planetary gear DP, and the second clutch C is connected to the planetary gear DP on the side opposite to the planetary gear unit PU in the axial direction.
- the clutch drum 32 which is the transmission member on the input side of 2
- the transmission member 32 on the input side of the carrier CR1 and the second clutch C 2 and the input shaft 12 can be connected without complicating the members.
- the hub member 116 of the first brake B-1 and the transmission member 104 connected thereto are connected to the sun gear S2 on the side opposite to the planetary gear DP in the planetary gear unit PU,
- the hub member 116 and the transmission member 104 of the brake B-1 can be connected to the sun gear S2 without complicating the members, and the automatic transmission 1 for the vehicle can be connected.
- the planetary gear DP supports a sun gear S1 whose rotation is always fixed with respect to the case 4, a pi-on gear P1, and a pi-on gear P2, and a carrier that is always connected to the input shaft 12.
- CR1 and the pinion gear P2 are meshed and output at reduced speed. Since it is comprised of the ring gear Rl, it is possible to output from the ring gear R1 the decelerated rotation obtained by decelerating the input rotation of the input shaft 12.
- the planetary gear unit PU includes a sun gear S2, a sun gear S3, a short pinion P3 that meshes with the sun gear S3, and a long pinion P4 that meshes with the sun gear S2 and meshes with the short peer P3, It consists of a radio gear type planetary gear unit PU having a carrier CR2 that rotatably supports the short pinion P3 and the long pinion P4, and a ring gear R3 that meshes with the long pinion P4. While it is possible to connect the rotating element and the output side member of each clutch or brake without complicating the members, the high rotating speed of each rotating element can be prevented and a good gear ratio can be obtained. be able to.
- the first clutch C-1 is engaged and the second brake B-2 is locked to engage the first forward speed
- the first clutch C-1 is engaged and the first brake
- the second forward speed is established.
- the third forward speed is established, and the first clutch C-1 is engaged.
- the fourth clutch C-4 are engaged with the fourth forward speed, and the first clutch C-1 and the second clutch C-2 are engaged with the fifth forward speed. 6th forward speed by engaging clutch C-2 and 4th clutch C-4, 7th forward speed by engaging 2nd clutch C-2 and 3rd clutch C-3
- the forward eighth gear is engaged, and the third clutch C-3 or the fourth clutch C-4 is engaged. More reverse gear to lock the second brake B- 2, can be achieved, respectively.
- the vertical axis indicates the rotational speeds of the sun gear S2, sun gear S3, carrier CR2, and ring gear R3 of the planetary gear unit PU
- the horizontal axis indicates the gears of the sun gear S2, sun gear S3, carrier CR2, and ring gear R3.
- the sun gear S2 is positioned at the end of the lateral direction, and is configured correspondingly to the carrier CR2, the ring gear R3 connected to the counter gear 15, and the sun gear S3 in this order. Can do.
- FIG. 12 is a sectional view showing the automatic transmission 1 according to the seventh embodiment. is there.
- parts having the same configuration as the automatic transmission 1 according to the second embodiment are given the same reference numerals to simplify the description.
- the automatic transmission 1 according to the seventh embodiment is the same as the automatic transmission 1 according to the second embodiment.
- the transmission mechanism 2 is configured by being substantially reversed in the (axial direction).
- hydraulic servo 20 of first clutch C 1 is disposed on the opposite side of planetary gear unit PU from planetary gear DP in the axial direction, and hydraulic servo 40 of third clutch C-3 is used.
- the hydraulic servo 30 of the second clutch C-2 and the counter gear 15 are arranged between the planetary gear DP and the planetary gear unit PU in the axial direction, and the hydraulic servo 50 of the fourth clutch C4 and the first brake B-1
- the hydraulic servo 60 is arranged on the opposite side of the planetary gear DP in the axial direction with respect to the planetary gear unit PU.
- the fourth clutch C-4 is arranged so as to be interposed on the transmission path connecting the input shaft 12 and the sun gear S2, and the second clutch C-4 is arranged.
- Arrange 2 to be on the transmission path connecting between carrier CR1 and carrier CR2, and connect the output transmission member 103 of the second clutch C-2 to the planetary gear DP in the axial direction of the planetary gear unit PU. Since it is connected to the carrier CR2 on the side, the member that wraps the planetary gear unit PU can be dispensed with. Thereby, the compactness in the radial direction of the vehicle automatic transmission 1 can be achieved.
- the transmission member that requires high rigidity can be shortened, the weight can be reduced, and the controllability of the vehicle automatic transmission 1 can be improved. Furthermore, it can be configured to easily discharge the supplied lubricating oil, and cooling performance can be ensured. In addition, the assembly of the vehicle automatic transmission 1 can be facilitated. Furthermore, depending on the arrangement structure of each clutch, a support wall 120 may be provided to enable the configuration in which the hydraulic fluid for the clutch is supplied from the support wall 120, thereby reducing the number of seal rings. Can reduce the sliding resistance of the seal ring. Thus, the power transmission efficiency of the vehicle automatic transmission i 7 can be improved.
- the hydraulic servo 30 of the second clutch C 2 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, the hydraulic servo 30 of the second clutch C 2 is placed in the support wall 120. It is possible to supply the hydraulic oil to the oil passage provided in the oil passage. As a result, the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case where hydraulic oil is supplied. The power transmission efficiency as the dynamic transmission 1 can be improved.
- the friction plate 51 of the fourth clutch C 4 is relatively outer circumferential. Since the friction plate 51 can be arranged on the side and the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of friction plates can be reduced. Furthermore, it is possible to supply hydraulic oil to the hydraulic servo 50 of the fourth clutch C-4 also in an oil passage provided in the box portion 3d connected to one end of the case 4. As a result, the oil passage provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. The power transmission efficiency of the automatic transmission 1 can be improved.
- the hydraulic servo 40 of the third clutch C 3 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, the planetary gear PU is opposite to the planetary gear PU with respect to the planetary gear DP.
- the output of the third clutch C-3 which can shorten the distance between the third clutch C-3 and the planetary gear unit PU and requires strength to transmit high torque,
- the side transmission member 101 can be shortened. As a result, it is possible to achieve light weight and improve controllability as the vehicle automatic transmission 1.
- the hydraulic servo 20 of the first clutch C-1 is disposed on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, the hydraulic servo 20 of the first clutch C-1 is connected to the hydraulic servo 20 of the case 4. It is possible to supply oil passage force hydraulic oil provided in the boss 3b connected to one end. As a result, the oil passage power provided in the input shaft 12 can also reduce the number of seal rings compared to the case of supplying hydraulic oil, and the sliding resistance of the seal rings can be reduced. As a result, the power transmission efficiency of the vehicle automatic transmission i 7 can be improved.
- the first brake B-1 that can lock the rotation of the sun gear S2 with respect to the case 4 is provided, and the hydraulic servo 60 of the first brake B-1 is Since it is arranged on the opposite side in the axial direction, the locking force transmission member of the first brake B-1 and the sun gear S2 can be connected without complicating the members, and the vehicle automatic transmission 17 can be compactly connected. can do.
- the transmission member 103 on the output side of the second clutch C-2 is connected to the third and first clutches C-3 and C-1.
- the output side transmission member 101, 102 is connected to the carrier CR2 through the outer peripheral side, and the output member 104 of the fourth clutch C-4 and the transmission member 101 of the output side of the third clutch C-3 are:
- the transmission member 104 on the output side of the fourth clutch C4, the output member 101 on the output side of the third clutch C-3, and the sun gear S2 are connected to the sun gear S2 and rotate integrally therewith.
- the transmission member 104 is disposed on the output side of the first clutch C 1 on the inner peripheral side of the transmission member 103 on the output side of the second clutch C-2.
- the diameter of the transmission member 104 on the output side of the fourth clutch C-4 can be made smaller than the diameter of the transmission member 103 on the output side of the second clutch C-2.
- the third and first clutches C-3, C-1 are arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the outputs of the third and first clutches C-3, C-1 are provided.
- Side transmission members 101 and 102 are connected to the sun gear S2 and sun gear S3, respectively, and the fourth clutch C-4 is arranged on the side opposite to the planetary gear DP in the axial direction with respect to the planetary gear unit PU.
- the transmission member 104 on the output side of C-4 is connected to the sun gear S2, and the second clutch C2 is arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the transmission member on the output side of the second clutch C-2 103, 3rd and 1st clutch C -Since it is connected to the carrier CR2 through the outer peripheral side of the transmission member 101, 102 on the output side of 3, C—l, the fourth rotation speed is higher than that of the transmission member 103 on the output side of the second clutch C-2.
- the diameter of the transmission member 104 on the output side of the fourth clutch C 4 is set to the diameter of the transmission member 103 on the output side of the second clutch C-2. It can be made smaller, and lighter weight can be achieved than when the outer peripheral side is used. In addition, since inertia (inertia force) can be reduced as compared with the case of the outside, the vehicle automatic transmission 1 can improve control performance.
- the friction plate 51 of the fourth clutch C-4 is arranged relatively on the outer peripheral side compared to the hydraulic servo 50 of the fourth clutch C4 arranged between the planetary gear unit PU and the planetary gear DP. Since the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of the friction plates 51 can be reduced. In addition, the distance between the third and first clutches C-3, C-1 and the planetary gear unit PU can be shortened, and the third and first clutches C-3, which are strong enough to transmit high torque, are required. , C-1 output side transmission members 101 and 102 can be shortened. As a result, a light weight can be achieved, and the controllability of the vehicle automatic transmission 1 can be improved.
- hydraulic oil can be supplied to the hydraulic servo 50 of the fourth clutch C-4 from, for example, an oil passage c50 provided in the boss portion 3b connected to the side wall 3a of the case 4. .
- the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal ring as compared with the case of supplying hydraulic oil.
- the power transmission efficiency of the transmission 1 can be improved.
- the transmission member on the input side of the fourth clutch C-4 it is connected to the input shaft 12 and the intermediate shaft 13 that pass through the inner peripheral side of the planetary gear unit PU, and the transmission on the input side of the fourth clutch C4.
- Part of the member is configured as the clutch drum 52 of the hydraulic servo 50 of the fourth clutch C—4, so that the transmission member on the output side of the fourth clutch C—4 is configured as the clutch drum of the hydraulic servo 50. Since the clutch drum of the hydraulic servo 50 can also serve as a power transmission member from the input shaft 12, it can be configured compactly in the axial direction.
- the planetary gear unit PU and the planetary gear are connected to the ring gear R3.
- a counter gear 15 disposed between the DP and the axial direction is provided.
- the counter gear 15 is connected to a support wall 120 extending from the case 4 and has a support portion 120a for supporting the counter gear 15.
- the second hub member 112 is connected to the carrier CR1 through the outer peripheral sides of the third and first clutches C-3, C-1, and a part of the transmission member 103 on the output side of the second clutch C-2 is connected to the carrier CR1.
- the second clutch C-2 is configured as a clutch drum 32 of the hydraulic servo 30 of the second clutch C-2, and the hydraulic servo 30 is disposed on the support portion 120a between the axial direction of the planetary gear DP and the counter gear 15, so that the second clutch C — It is possible to supply hydraulic oil to the hydraulic servo 30 of 2 also with the oil passage c30 force provided in the support part 120a. As a result, the number of seal rings can be reduced and the sliding resistance of the seal rings can be reduced, compared with the case where, for example, the oil passage force hydraulic oil provided in the input shaft 12 is supplied. The power transmission efficiency of the automatic transmission 1 can be improved.
- the counter shaft 81 is provided in parallel to the input shaft 12 and connected via the counter gear 15 connected to the ring gear R3, and the output rotation from the ring gear R3 is transmitted via the counter gear 15.
- the vehicle automatic transmission 1 can be suitably used for an FF type vehicle.
- the counter gear 15 is arranged between the planetary gear unit PU and the planetary gear DP in the axial direction, and is supported by the support portion 120a connected to the support wall 120 extending from the case 4,
- the counter gear 15 can be prevented from moving away from the input side force in the axial direction.
- the counter shaft portion 80 and the differential gear portion 90 can be brought closer to the torque converter 7 side, so that the vehicle automatic transmission 1 can be compacted.
- the carrier CR1 is connected to the input shaft 12 on the planetary gear unit PU side with respect to the planetary gear DP, and the second clutch C is connected to the planetary gear DP on the side opposite to the planetary gear unit PU in the axial direction.
- the hub member 112 which is the transmission member on the input side of 2
- the transmission member 112 on the input side of the carrier CR1 and the second clutch C 2 and the input shaft 12 can be connected without complicating the members.
- the vehicle automatic transmission 1 can be compacted.
- the hub member 116 of the first brake B-l and the transmission member 104 connected thereto are connected to the sun gear S2 on the opposite side of the planetary gear DP in the planetary gear unit PU in the axial direction.
- the hub member 116 and transmission member 104 of the brake B-1 and the sun gear S2 can be connected without complicating the members, and the vehicle automatic transmission 1 can be connected.
- the planetary gear DP is a carrier that supports the sun gear S1 whose rotation is always fixed with respect to the case 4 and the pin-on gear P1 and the pin-on gear P2 so as to be rotatable and is always connected to the input shaft 12. Since it comprises CR1 and a ring gear R1 that meshes with the pinion gear P2 and outputs a reduced speed rotation, it is possible to output a reduced speed rotation that reduces the input rotation of the input shaft 12 from the ring gear R1.
- the planetary gear unit PU includes a sun gear S2, a sun gear S3, a short pinion P3 that meshes with the sun gear S3, and a long pinion P4 that meshes with the sun gear S2 and meshes with the short peer P3, It consists of a radio gear type planetary gear unit PU having a carrier CR2 that rotatably supports the short pinion P3 and the long pinion P4, and a ring gear R3 that meshes with the long pinion P4. While it is possible to connect the rotating element and the output side member of each clutch or brake without complicating the members, the high rotating speed of each rotating element can be prevented and a good gear ratio can be obtained. be able to.
- first clutch C-1 is engaged and the second brake B-2 is locked to engage the first forward speed
- first clutch C-1 is engaged and the first brake
- the second forward speed is established.
- the third forward speed is established, and the first clutch C-1 is engaged.
- the fourth clutch C-4 are engaged with the fourth forward speed
- the first clutch C-1 and the second clutch C-2 are engaged with the fifth forward speed. 6th forward speed by engaging clutch C-2 and 4th clutch C-4, 7th forward speed by engaging 2nd clutch C-2 and 3rd clutch C-3 Engage the second clutch C-2 and lock the first brake B-1 to engage the eighth forward speed, and engage the third clutch C-3 or the fourth clutch C-4.
- More reverse gear to lock the second brake B- 2 can be achieved, respectively.
- the vertical axis indicates the rotation speed of sun gear S2, sun gear S3, carrier CR2, and ring gear R3 of planetary gear unit PU
- the horizontal axis indicates the gears of sun gear S2, sun gear S3, carrier CR2, and ring gear R3.
- the sun gear S2 is positioned at the end of the lateral direction, and is configured corresponding to the carrier CR2 and the ring gear R3 connected to the counter gear 15 and the sun gear S3 in this order. Can do.
- FIG. 13 is a sectional view showing the automatic transmission 1 according to the eighth embodiment.
- the automatic transmission 1 according to the eighth embodiment is the same as the automatic transmission 1 according to the third embodiment.
- the first to fourth clutches C 1 to C 4 and the first and second brakes B-1 to B-2, planetary gear DP, planetary gear unit PU, counter gear 15, etc. are arranged by inverting the left and right direction (axial direction) substantially, that is, shifting mechanism 2 is set to the left and right direction.
- the transmission mechanism 2 is configured by being substantially reversed in the (axial direction).
- the fourth clutch C-4 is connected to the input shaft 12 and the sun gear.
- the second clutch C-2 is placed on the transmission path connecting between the carrier CR1 and the carrier CR2, and the second clutch C-2 is arranged on the transmission path connecting to the S2. Since the output transmission member 103 of the clutch C-2 is connected to the carrier CR2 on the planetary gear DP in the axial direction of the planetary gear unit PU, a member for enclosing the planetary gear unit PU can be eliminated. As a result, the radial direction of the vehicle automatic transmission 1 Compactness can be achieved. In addition, it is possible to shorten the transmission member that requires high rigidity, to reduce the weight, and to improve the controllability as the vehicle automatic transmission 1.
- a support wall 120 can be provided to enable the configuration in which the hydraulic fluid for the clutch is supplied from the support wall 120, thereby reducing the number of seal rings. Therefore, the sliding resistance of the seal ring can be reduced, and the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- the support wall 120 is connected to the hydraulic servo 30 of the second clutch C2.
- the oil passage provided inside can also be able to supply hydraulic oil.
- the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case where hydraulic oil is supplied.
- the power transmission efficiency as the dynamic transmission 1 can be improved.
- the friction plate 51 of the fourth clutch C 4 is relatively outer circumferential. Since the friction plate 51 can be arranged on the side and the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of friction plates can be reduced. Furthermore, it is possible to supply hydraulic oil to the hydraulic servo 50 of the fourth clutch C-4 also in an oil passage provided in the box portion 3d connected to one end of the case 4. As a result, the oil passage provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. The power transmission efficiency of the automatic transmission 1 can be improved.
- the hydraulic servo 40 of the third clutch C 3 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, the planetary gear PU is opposite to the planetary gear PU with respect to the planetary gear DP.
- the output of the third clutch C-3 which can shorten the distance between the third clutch C-3 and the planetary gear unit PU and requires strength to transmit high torque,
- the side transmission member 101 can be shortened. This makes it light As a result, it is possible to improve the controllability of the vehicle automatic transmission 1.
- the hydraulic servo 20 of the first clutch C 1 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, the planetary gear PU is opposite to the planetary gear PU with respect to the planetary gear DP.
- the output of the first clutch C-1 which can reduce the distance between the first clutch C-1 and the planetary gear unit PU, and requires strength to transmit high torque,
- the side transmission member 102 can be shortened. As a result, it is possible to achieve light weight and improve controllability as the vehicle automatic transmission 1.
- the first brake B-1 that can freely lock the rotation of the sun gear S2 with respect to the case 4 is provided, and the hydraulic servo 60 of the first brake B-1 is connected to the planetary gear unit PU with the planetary gear DP. Since it is arranged on the opposite side in the axial direction, the locking force transmission member of the first brake B-1 and the sun gear S2 can be connected without complicating the members.
- the output-side transmission member 103 is connected to the carrier CR2 through the outer peripheral side of the output-side transmission members 101, 102 of the third and first clutches C-3, C-1, and the fourth clutch C-4.
- the output-side transmission member 104 and the output-side transmission member 101 of the third clutch C-3 are connected to the sun gear S2, and the output-side transmission member 104 of the fourth clutch C4, which rotates integrally therewith, Since the transmission member 101 on the output side of the third clutch C-3 and the sun gear S2 are arranged on the inner peripheral side with respect to the transmission member 102 on the output side of the first clutch C-1, the second clutch C-2
- the transmission member 104 on the output side of the fourth clutch C-4, which rotates at a higher speed than the transmission member 103 on the output side of the first output is located on the inner peripheral side of the transmission member 103 on the output side of the second clutch C-2.
- the inner diameter side of the output member 102 on the output side of the clutch C 1 is set to the inner peripheral side. And it is a child less than the diameter of the output side of the transfer member 103 of the latch C-2, it is possible to reduce the weight I spoon than when disposed on the outer peripheral side. In addition, since inertia (inertial force) can be reduced as compared with the case where it is arranged on the outer peripheral side, the controllability of the vehicle automatic transmission 1 can be improved. [0294] Also, the third and first clutches C-3, C-1 are arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the outputs of the third and first clutches C-3, C-1 are provided.
- Side transmission members 101 and 102 are connected to the sun gear S2 and sun gear S3, respectively, and the fourth clutch C-4 is arranged on the side opposite to the planetary gear DP in the axial direction with respect to the planetary gear unit PU.
- the transmission member 104 on the output side of C-4 is connected to the sun gear S2, and the second clutch C2 is arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the transmission member on the output side of the second clutch C-2 103 is connected to the carrier CR2 through the outer peripheral sides of the output members 101, 102 on the output side of the third and first clutches C-3, C-1, so that the output on the output side of the second clutch C-2 is transmitted.
- the output member 104 on the output side 4 is the inner peripheral side
- the diameter of the output member 104 on the output side of the fourth clutch C 4 is larger than the diameter of the output member 103 on the output side of the second clutch C-2. It can be made smaller and lighter than the outer peripheral side.
- the inertia inertial force
- the friction plate 51 of the fourth clutch C-4 is arranged relatively on the outer peripheral side compared to the hydraulic servo 50 of the fourth clutch C4 arranged between the planetary gear unit PU and the planetary gear DP. Since the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of the friction plates 51 can be reduced. In addition, the distance between the third and first clutches C-3, C-1 and the planetary gear unit PU can be shortened, and the third and first clutches C-3, which are strong enough to transmit high torque, are required. , C-1 output side transmission members 101 and 102 can be shortened. As a result, a light weight can be achieved, and the controllability of the vehicle automatic transmission 1 can be improved.
- hydraulic oil can be supplied to the hydraulic servo 50 of the fourth clutch C-4 from, for example, an oil passage c50 provided in the boss portion 3b connected to the side wall 3a of the case 4. .
- the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal ring as compared with the case of supplying hydraulic oil.
- the power transmission efficiency of the transmission 1 can be improved.
- the transmission member on the input side of the fourth clutch C-4 the planetary gear unit PU Since it is connected to the input shaft 12 and the intermediate shaft 13 passing through the circumferential side, a part of the transmission member on the input side of the fourth clutch C 4 is configured as the clutch drum 52 of the hydraulic servo 50 of the fourth clutch C-4.
- the clutch drum of the hydraulic servo 50 can also serve as the power transmission member from the input shaft 12 as compared with the case where the transmission member on the output side of the fourth clutch C-4 is configured as a clutch drum of the hydraulic servo 50. Therefore, it can be made compact in the axial direction.
- the counter gear 15 is connected to the ring gear R3 and is arranged between the planetary gear unit PU and the planetary gear DP in the axial direction.
- the counter gear 15 is connected to the support wall 120 extending from the case 4, and the counter gear. 15 and supporting the hub member 112 of the second clutch C-2 through the outer peripheral side of the third and first clutches C-3, C-1, and to the carrier CR1,
- a part of the transmission member 103 on the output side of the second clutch C-2 is configured as a clutch drum 32 of the hydraulic servo 30 of the second clutch C-2, and the hydraulic servo 30 is connected to the shaft of the planetary gear DP and the counter gear 15.
- the transmission member 102 on the output side of the first clutch C-1 is connected to the sun gear S3, and a part of the transmission member 102 on the output side of the first clutch C-1 is connected to the first clutch C-
- the hydraulic servo 20 is arranged on the support 120a between the planetary gear DP and the axial direction of the hydraulic servo 30 of the second clutch C-2.
- the output member 101 of the clutch C-3 output side is connected to the sun gear S2, and a part of the output member 101 of the third clutch C-3 is connected to the hydraulic servo 40 of the third clutch C-3.
- the hydraulic servo 40 is disposed between the planetary gear DP and the axial direction of the hydraulic servo 20 of the first clutch C—1, the hydraulic servo 20 of the first clutch C 1 is connected to the case 4 from the case 4. Operates from extended support wall 120 and oil channel c20 provided in support 120a It may be possible to supply oil. Thus, for example, in the input shaft 12 Compared with the case where hydraulic oil is supplied with hydraulic oil, the number of seal rings can be reduced, and the sliding resistance of the seal rings can be reduced.
- the hydraulic servo 40 of the third clutch C 3 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, for example, the planetary gear unit PU is disposed opposite to the planetary gear unit PU in the axial direction.
- the distance between the third clutch C-3 and the planetary gear unit PU can be shortened, and transmission on the output side of the third clutch C3, which requires strength to transmit high torque, is possible.
- the member 101 can be shortened. As a result, light weight can be achieved, and controllability can be improved as a vehicle automatic transmission.
- a counter shaft 81 is provided which is arranged in parallel to the input shaft 12 and connected via the counter gear 15 connected to the ring gear R3, and the output rotation from the ring gear R3 1S via the counter gear 15 Since it is transmitted to the counter shaft 81, the vehicle automatic transmission 1 can be suitably used for an FF type vehicle.
- the counter gear 15 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, and is supported by the support portion 120a connected to the support wall 120 extending from the case 4.
- the counter gear 15 can be prevented from moving away from the input side force in the axial direction.
- the counter shaft portion 80 and the differential gear portion 90 can be brought closer to the torque converter 7 side, so that the vehicle automatic transmission Compact 1
- the carrier CR1 is connected to the input shaft 12 on the planetary gear unit PU side with respect to the planetary gear DP, and the second clutch C is connected to the planetary gear DP on the side opposite to the planetary gear unit PU in the axial direction.
- 2 is connected to the hub member 112, which is the transmission member on the input side, so that the transmission member 112 on the input side of the carrier CR1 and the second clutch C2 and the input shaft 12 can be connected without complicating the members.
- the hub member 116 of the first brake B-1 and the transmission member 104 connected thereto are connected to the sun gear on the opposite side of the planetary gear DP in the planetary gear unit PU in the axial direction. Therefore, the hub member 116 and transmission member 104 of the first brake B-1 and the sun gear S2 can be connected without complicating the members, and the vehicle automatic transmission 1 can be connected.
- the planetary gear DP is a carrier that supports the sun gear S1 whose rotation is always fixed with respect to the case 4, the pin-on gear P1, and the pin-on gear P2 so as to be rotatable and is always connected to the input shaft 12. Since it comprises CR1 and a ring gear R1 that meshes with the pinion gear P2 and outputs a reduced speed rotation, it is possible to output a reduced speed rotation that reduces the input rotation of the input shaft 12 from the ring gear R1.
- the planetary gear unit PU includes a sun gear S2, a sun gear S3, a short pinion P3 that meshes with the sun gear S3, a long pinion P4 that meshes with the sun gear S2, and meshes with the short peer P3, It consists of a radio gear type planetary gear unit PU having a carrier CR2 that rotatably supports the short pinion P3 and the long pinion P4, and a ring gear R3 that meshes with the long pinion P4. While it is possible to connect the rotating element and the output side member of each clutch or brake without complicating the members, the high rotating speed of each rotating element can be prevented and a good gear ratio can be obtained. be able to.
- the first clutch C-1 is engaged and the second brake B-2 is locked to engage the first forward speed
- the first clutch C-1 is engaged and the first brake
- the second forward speed is established.
- the third forward speed is established, and the first clutch C-1 is engaged.
- the fourth clutch C-4 are engaged with the fourth forward speed, and the first clutch C-1 and the second clutch C-2 are engaged with the fifth forward speed. 6th forward speed by engaging clutch C-2 and 4th clutch C-4, 7th forward speed by engaging 2nd clutch C-2 and 3rd clutch C-3
- the forward eighth gear is engaged, and the third clutch C-3 or the fourth clutch C-4 is engaged. More reverse gear to lock the second brake B- 2, can be achieved, respectively.
- the vertical axis indicates the number of rotations of the sun gear S2, sun gear S3, carrier CR2, and ring gear R3 of the planetary gear unit PU, and the horizontal axis indicates the sun gear S2, sun gear.
- the sun gear S2 is positioned at the end of the lateral direction, and the ring gear R3 is connected to the carrier CR2 and counter gear 15 in order. It can be configured to correspond to the sun gear S3.
- FIG. 14 is a sectional view showing an automatic transmission 1 according to the ninth embodiment.
- the automatic transmission 1 according to the ninth embodiment is the same as the automatic transmission 1 according to the fourth embodiment.
- the transmission mechanism 2 is configured by being substantially reversed in the (axial direction).
- the planetary gear unit PU is disposed on the opposite side of the planetary gear unit PU with respect to the DP.
- the hydraulic servo 20 of the first clutch C—1, the hydraulic servo 30 of the second clutch C—2, and the counter gear 15 are connected to the planetary gear DP and the planetary gear.
- the hydraulic servo 50 of the fourth clutch C 4 and the hydraulic servo 60 of the first brake B—1 are arranged on the opposite side of the planetary gear DP with respect to the planetary gear unit PU. Has been.
- the fourth clutch C-4 is connected to the input shaft 12 and the sun gear.
- the second clutch C-2 is placed on the transmission path connecting between the carrier CR1 and the carrier CR2, and the second clutch C-2 is arranged on the transmission path connecting to the S2. Since the output transmission member 103 of the clutch C-2 is connected to the carrier CR2 on the planetary gear DP side in the axial direction of the planetary gear unit PU, a member for enclosing the planetary gear unit PU can be eliminated. As a result, the automatic transmission 1 for the vehicle
- a support wall 120 can be provided to enable the configuration in which the hydraulic fluid for the clutch is supplied from the support wall 120, thereby reducing the number of seal rings. Therefore, the sliding resistance of the seal ring can be reduced, and the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- the support wall 120 is connected to the hydraulic servo 30 of the second clutch C2.
- the oil passage provided inside can also be able to supply hydraulic oil.
- the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case where hydraulic oil is supplied.
- the power transmission efficiency as the dynamic transmission 1 can be improved.
- the friction plate 51 of the fourth clutch C 4 is relatively outer circumferential. Since the friction plate 51 can be arranged on the side and the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of friction plates can be reduced. Furthermore, it is possible to supply hydraulic oil to the hydraulic servo 50 of the fourth clutch C-4 also in an oil passage provided in the box portion 3d connected to one end of the case 4. As a result, the oil passage provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. The power transmission efficiency of the automatic transmission 1 can be improved.
- the hydraulic servo 40 of the third clutch C 3 is arranged on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, one end of the case 4 is connected to the hydraulic servo 40 of the third clutch C-3. It is possible to supply the oil passage force hydraulic oil provided in the boss 3b connected to the. As a result, the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. Improve power transmission efficiency as an automatic transmission 1 Togashi.
- the hydraulic servo 20 of the first clutch C-1 is arranged between the planetary gear unit PU and the planetary gear DP in the axial direction, the planetary gear PU is opposite to the planetary gear PU in the axial direction.
- the distance between the first clutch C-1 and the planetary gear unit PU can be shortened compared to the case where it is arranged on the side, and the strength of the first clutch C-1 that requires strength to transmit high torque can be reduced.
- the output side transmission member 102 can be shortened. As a result, it is possible to achieve light weight and improve controllability as the vehicle automatic transmission 1.
- the first brake B-1 that can freely lock the rotation of the sun gear S2 with respect to the case 4 is provided, and the hydraulic servo 60 of the first brake B-1 is connected to the planetary gear unit PU with the planetary gear DP. Since it is arranged on the opposite side in the axial direction, the locking force transmission member of the first brake B-1 and the sun gear S2 can be connected without complicating the members.
- the output-side transmission member 103 is connected to the carrier CR2 through the outer peripheral side of the output-side transmission members 101, 102 of the third and first clutches C-3, C-1, and the fourth clutch C-4.
- the output-side transmission member 104 and the output-side transmission member 101 of the third clutch C-3 are connected to the sun gear S2, and the output-side transmission member 104 of the fourth clutch C4, which rotates integrally therewith, Since the transmission member 101 on the output side of the third clutch C-3 and the sun gear S2 are arranged on the inner peripheral side with respect to the transmission member 102 on the output side of the first clutch C-1, the second clutch C-2
- the transmission member 104 on the output side of the fourth clutch C-4, which rotates at a higher speed than the transmission member 103 on the output side of the first output is located on the inner peripheral side of the transmission member 103 on the output side of the second clutch C-2.
- the inner diameter side of the output member 102 on the output side of the clutch C 1 is set to the inner peripheral side. And it is a child less than the diameter of the output side of the transfer member 103 of the latch C-2, it is possible to reduce the weight I spoon than when disposed on the outer peripheral side. In addition, since inertia (inertial force) can be reduced as compared with the case where it is arranged on the outer peripheral side, the controllability of the vehicle automatic transmission 1 can be improved.
- the third and first clutches C-3 and C-1 are connected to the planetary gear unit PU.
- the transmission members 101 and 102 on the output side of the third and first clutches C-3 and C-1 are connected to the sun gear S2 and sun gear S3, respectively, and the fourth clutch C-4 is connected.
- the planetary gear unit PU is disposed on the opposite side of the planetary gear DP in the axial direction, the transmission member 104 on the output side of the fourth clutch C-4 is connected to the sun gear S2, and the second clutch C2 is connected to the planetary gear unit PU.
- the transmission member 103 on the output side of the second clutch C-2 is connected to the outer periphery of the transmission members 101 and 102 on the output side of the third and first clutches C-3 and C-1. Because the transmission member 104 on the output side of the fourth clutch C4, which rotates faster than the transmission member 103 on the output side of the second clutch C-2, is on the inner peripheral side. 4th clutch C 4 output side transmission member 104 of And it can be smaller than the diameter of the second clutch C-2 on the output side of the transmission member 103, it is possible to reduce the weight I spoon than when the outer peripheral side. In addition, the inertia (inertial force) can be reduced compared to the case of the outside, so the vehicle automatic transmission 1 and
- the friction plate 51 of the fourth clutch C-4 is arranged on the relatively outer side compared to the hydraulic servo 50 of the fourth clutch C4 arranged between the planetary gear unit PU and the planetary gear DP. Since the area of the friction plate 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of the friction plates 51 can be reduced. In addition, the distance between the third and first clutches C-3, C-1 and the planetary gear unit PU can be shortened, and the third and first clutches C-3, which are strong enough to transmit high torque, are required. , C-1 output side transmission members 101 and 102 can be shortened. As a result, a light weight can be achieved, and the controllability of the vehicle automatic transmission 1 can be improved.
- hydraulic oil can be supplied to the hydraulic servo 50 of the fourth clutch C-4 from, for example, an oil passage c50 provided in the boss portion 3b connected to the side wall 3a of the case 4. .
- the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal ring as compared with the case of supplying hydraulic oil.
- the power transmission efficiency of the transmission 1 can be improved.
- the transmission member on the input side of the fourth clutch C-4 it is connected to the input shaft 12 and the intermediate shaft 13 that pass through the inner peripheral side of the planetary gear unit PU, and the input side of the fourth clutch C 4 Part of the transmission member is configured as the clutch drum 52 of the hydraulic clutch 50 of the fourth clutch C—4. Therefore, the transmission member on the output side of the fourth clutch C—4 is configured as the clutch drum of the hydraulic servo 50.
- the clutch drum of the hydraulic servo 50 can also serve as a power transmission member from the input shaft 12, so that it can be made compact in the axial direction.
- the counter gear 15 is connected to the ring gear R3 and is arranged between the planetary gear unit PU and the planetary gear DP in the axial direction.
- the counter gear 15 is connected to the support wall 120 extending from the case 4, and the counter gear. 15 and supporting the hub member 112 of the second clutch C-2 through the outer peripheral side of the third and first clutches C-3, C-1, and to the carrier CR1,
- a part of the transmission member 103 on the output side of the second clutch C-2 is configured as a clutch drum 32 of the hydraulic servo 30 of the second clutch C-2, and the hydraulic servo 30 is connected to the shaft of the planetary gear DP and the counter gear 15.
- a part of the member is configured as a clutch drum 22 of the hydraulic servo 20 of the first clutch C—1, and the hydraulic servo 20 is arranged between the planetary gear DP and the hydraulic servo 30 of the second clutch C 2 in the axial direction. Since it is arranged on the support part 120a, the hydraulic pressure of the third clutch C 3
- the turbo 40 it is possible to be able to supply feed the working oil from the oil passage c40 provided in the boss portion 3b that is linked to the side wall 3a of the case 4.
- the hydraulic support of the third clutch C 3 Compared to the case where the robot 40 is disposed on the input shaft 12 away from the boss 3b and hydraulic oil is supplied through the oil passage in the input shaft 12, the oil passage in the input shaft 12 is not interposed.
- the oil path length can be shortened and the controllability of the vehicle automatic transmission 1 can be improved.
- the oil passage provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil.
- the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- the counter shaft 81 is arranged in parallel to the input shaft 12 and connected via the counter gear 15 connected to the ring gear R3, and the output rotation from the ring gear R3 1S via the counter gear 15 Since it is transmitted to the counter shaft 81, the vehicle automatic transmission 1 can be suitably used for an FF type vehicle.
- the counter gear 15 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, and is supported by the support portion 120a connected to the support wall 120 extending from the case 4.
- the counter gear 15 can be prevented from moving away from the input side force in the axial direction.
- the counter shaft portion 80 and the differential gear portion 90 can be brought closer to the torque converter 7 side, so that the vehicle automatic transmission Compact 1
- the carrier CR1 is connected to the input shaft 12 on the planetary gear unit PU side with respect to the planetary gear DP, and the second clutch C is connected to the planetary gear DP on the side opposite to the planetary gear unit PU in the axial direction.
- 2 is connected to the hub member 112, which is the transmission member on the input side, so that the transmission member 112 on the input side of the carrier CR1 and the second clutch C2 and the input shaft 12 can be connected without complicating the members.
- hub member 116 of the first brake B-1 and the transmission member 104 connected thereto are connected to the gear S2 on the opposite side of the planetary gear DP in the planetary gear unit PU to the sun gear S2.
- Hub member 116 and transmission member 104 of brake B-1 Gear S2 can be connected without complicating parts, and the vehicle automatic transmission 1 can be connected.
- the planetary gear DP supports the sun gear S1 whose rotation is always fixed with respect to the case 4, the pi-on gear P1, and the pi-on gear P2 so as to be rotatable and is always coupled to the input shaft 12. Since it comprises CR1 and a ring gear R1 that meshes with the pinion gear P2 and outputs a reduced speed rotation, it is possible to output a reduced speed rotation that reduces the input rotation of the input shaft 12 from the ring gear R1.
- the planetary gear unit PU includes a sun gear S2, a sun gear S3, a short pinion P3 that meshes with the sun gear S3, a long pinion P4 that meshes with the sun gear S2, and meshes with the short peer P3, Since each of the planetary gear units PU is comprised of a radio gear type planetary gear unit PU having a carrier CR2 that rotatably supports the short pinion P3 and the long pinion P4 and a ring gear R3 that meshes with the long pinion P4. While it is possible to connect the rotating element and the output side member of each clutch or brake without complicating the members, the high rotating speed of each rotating element can be prevented and a good gear ratio can be obtained. be able to.
- first clutch C-1 is engaged and the second brake B-2 is locked to engage the first forward speed
- first clutch C-1 is engaged and the first brake
- second forward speed is established.
- the third forward speed is established, and the first clutch C-1 is engaged.
- the fourth clutch C-4 are engaged with the fourth forward speed
- the first clutch C-1 and the second clutch C-2 are engaged with the fifth forward speed. 6th forward speed by engaging clutch C-2 and 4th clutch C-4, 7th forward speed by engaging 2nd clutch C-2 and 3rd clutch C-3
- the forward eighth gear is engaged, and the third clutch C-3 or the fourth clutch C-4 is engaged. More reverse gear to lock the second brake B- 2, can be achieved, respectively.
- the vertical axis indicates the rotation speed of sun gear S2, sun gear S3, carrier CR2, and ring gear R3 of planetary gear unit PU
- the horizontal axis indicates the gears of sun gear S2, sun gear S3, carrier CR2, and ring gear R3.
- the sun gear S2 can be configured to correspond to the ring gear R3 and the sun gear S3, which are positioned at the end in the lateral direction and sequentially connected to the carrier CR2 and the counter gear 15.
- FIG. 15 is a sectional view showing an automatic transmission 1 according to the tenth embodiment.
- the automatic transmission 1 according to the tenth embodiment is the automatic transmission according to the fifth embodiment.
- 4th clutch C—4 hydraulic servo 50, 1st clutch C—1 hydraulic servo 20 and 2nd clutch C—2 hydraulic servo are arranged on the opposite side of the gear DP from the planetary gear unit PU.
- 30 and counter gear 15 are arranged between the planetary gear DP and the planetary gear unit PU in the axial direction, and the hydraulic servo 60 of the first brake B-1 is opposite to the planetary gear DP in the axial direction with respect to the planetary gear PU.
- the fourth clutch C-4 is connected to the input shaft 12 and the sun gear.
- the second clutch C-2 is placed on the transmission path that connects between the carrier CR1 and the carrier CR2, and the second clutch C-2 is placed on the transmission path that connects the carrier S2. 2 Since the output side transmission member 103 of the latch C-2 is connected to the carrier CR2 on the planetary gear DP in the axial direction of the planetary gear unit PU, a member for enclosing the planetary gear unit PU can be eliminated. As a result, the radial direction of the vehicle automatic transmission 1
- the transmission member that requires high rigidity can be shortened, the weight can be reduced, and the controllability of the vehicle automatic transmission 1 can be improved.
- each clutch it is possible to arrange the support wall 120 and supply the hydraulic fluid of the clutch from the support wall 120, so that the number of seal rings can be reduced. As a result, the sliding resistance of the seal ring can be reduced, and the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- the support wall 120 is connected to the hydraulic servo 30 of the second clutch C2.
- the oil passage provided inside can also be able to supply hydraulic oil.
- the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case where hydraulic oil is supplied. The power transmission efficiency of the dynamic transmission 1 can be improved.
- the carrier CR1 and the fourth clutch C-4 A part of the members constituting the clutch drum 52 of the hydraulic servo 50 (that is, the clutch drum 52 and the side plate of the carrier CR1) can be shared, so that a reduction in size and weight can be achieved.
- the hydraulic servo 40 of the third clutch C-3 is disposed on the opposite side of the planetary gear unit PU from the planetary gear DP, the hydraulic servo 40 of the third clutch C-3 is connected to the case 4 of the case 4. It is possible to supply the oil passage force hydraulic oil provided in the boss 3b connected to one end. As a result, the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. Improving power transmission efficiency as automatic transmission 1 be able to.
- the hydraulic servo 20 of the first clutch C 1 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, the hydraulic servo 20 of the first clutch C 1 is placed in the support wall 120. It is possible to supply the hydraulic oil to the oil passage provided in the oil passage. As a result, the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case where hydraulic oil is supplied. The power transmission efficiency of the dynamic transmission 1 can be improved.
- the first brake B-1 that can freely lock the rotation of the sun gear S2 with respect to the case 4 is provided, and the hydraulic servo 60 of the first brake B-1 is connected to the planetary gear unit PU with the planetary gear DP. Since it is arranged on the opposite side in the axial direction, the locking force transmission member of the first brake B-1 and the sun gear S2 can be connected without complicating the members, and the vehicle automatic transmission 1 can be
- the output-side transmission member 103 is connected to the carrier CR2 through the outer peripheral side of the output-side transmission members 101, 102 of the third and first clutches C-3, C-1, and the fourth clutch C-4. And the transmission member 101 on the output side of the third clutch C-3 is connected to the sun gear S2 and transmits on the output side of the fourth clutch C-4 and the third clutch C-3 that rotate integrally. Since the member 101 and the sun gear S2 are arranged on the inner peripheral side with respect to the transmission member 102 on the output side of the first clutch C-1, the rotation speed is higher than that of the transmission member 103 on the output side of the second clutch C-2.
- the transmission member 101 on the output side of the fourth clutch C—4 is the output transmission member 102 on the output side of the first clutch C—1 on the inner peripheral side of the transmission member 103 on the output side of the second clutch C-2.
- the diameter of the transmission member 101 on the output side of the fourth clutch C-4 is set to the transmission member 103 on the output side of the second clutch C-2. And can be made smaller than the diameter, it is possible to reduce the weight I spoon than when disposed on the outer peripheral side.
- inertia inertial force
- the third and first clutches C-3, C-1 are arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the outputs of the third and first clutches C-3, C-1 are provided.
- Side transmission members 101 and 102 are connected to sun gear S2 and sun gear S3, respectively, and the fourth clutch C —4 is arranged on the planetary gear DP side with respect to the planetary gear unit PU, the transmission member 101 on the output side of the fourth clutch C—4 is connected to the sun gear S2, and the second clutch C-2 is connected to the planetary gear unit PU.
- the transmission member 103 on the output side of the second clutch C-2 is connected to the outer peripheral side of the transmission members 101 and 102 on the output side of the third and first clutches C-3 and C-1. Since it is connected to the carrier CR2 through the second clutch C-2, the output member 101 on the output side of the fourth clutch C-4, which is higher in rotation than the output member 103 on the output side, becomes the inner peripheral side. Therefore, the diameter of the transmission member 101 on the output side of the fourth clutch C 4 can be made smaller than the diameter of the transmission member 103 on the output side of the second clutch C-2, which is lighter than that on the outer peripheral side. Can be achieved. In addition, inertia (inertial force) can be reduced compared to the case of the outer peripheral side, so that the automatic transmission 1 for vehicles is more controllable.
- the transmission member on the input side of the fourth clutch C-4 it is directly connected to the carrier CR1, and is configured as a part of the hydraulic servo 50 of the fourth clutch C-4 with a part of the carrier CR1.
- Part of the components that make up the carrier CR1 and the hydraulic servo 50 of the fourth clutch C-4 can be shared. You can make a habit.
- the counter gear 15 is connected to the ring gear R3 and arranged between the planetary gear unit PU and the planetary gear DP in the axial direction.
- the counter gear 15 is connected to the support wall 120 extending from the case 4 and the counter gear. 15 and supporting the hub member 112 of the second clutch C-2 through the outer peripheral side of the third and first clutches C-3, C-1, and to the carrier CR1,
- a part of the transmission member 103 on the output side of the second clutch C-2 is configured as a clutch drum 32 of the hydraulic servo 30 of the second clutch C-2, and the hydraulic servo 30 is connected to the shaft of the planetary gear DP and the counter gear 15.
- a part of the member is configured as a clutch drum 22 of the hydraulic servo 20 of the first clutch C—1, and the hydraulic servo 20 is arranged between the planetary gear DP and the hydraulic servo 30 of the second clutch C 2 in the axial direction. Since it is arranged on the support part 120a, the hydraulic pressure of the third clutch C 3
- the turbo 40 it is possible to be able to supply feed the working oil from the oil passage c40 provided in the boss portion 3b that is linked to the side wall 3a of the case 4.
- the hydraulic servo 40 of the third clutch C 3 is disposed on the input shaft 12 away from the boss portion 3b, and hydraulic oil is supplied through the oil passage in the input shaft 12.
- the length of the oil passage can be shortened by the absence of the oil passage in the input shaft 12, and the controllability of the vehicle automatic transmission 1 can be improved.
- the oil passage provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil.
- the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- the counter shaft 81 is provided in parallel with the input shaft 12 and connected via the counter gear 15 connected to the ring gear R3, and the output rotation from the ring gear R3 is transmitted via the counter gear 15.
- the vehicle automatic transmission 1 can be suitably used for an FF type vehicle.
- the counter gear 15 is disposed between the planetary gear unit PU and the planetary gear DP in the axial direction, and is supported by the support portion 120a connected to the support wall 120 extending from the case 4.
- the counter gear 15 can be prevented from moving away from the input side force in the axial direction.
- the counter shaft portion 80 and the differential gear portion 90 can be brought closer to the torque converter 7 side, so that the vehicle automatic transmission Compact 1 Can.
- the carrier CR1 is connected to the input shaft 12 on the planetary gear unit PU side with respect to the planetary gear DP, and the second clutch C is connected to the planetary gear DP on the side opposite to the planetary gear unit PU in the axial direction.
- the hub member 112 which is the transmission member on the input side of 2
- the transmission member 112 on the input side of the carrier CR1 and the second clutch C 2 and the input shaft 12 can be connected without complicating the members.
- the hub member 116 of the first brake B-1 and the transmission member 104 connected thereto are connected to the sun gear S2 on the opposite side of the planetary gear DP in the planetary gear unit PU to the sun gear S2.
- the hub member 116 and the transmission member 104 of the brake B-1 and the sun gear S2 can be connected without complicating the members, and the automatic transmission 1 for the vehicle can be connected.
- the planetary gear DP is a carrier that supports the sun gear S1 whose rotation is always fixed with respect to the case 4, the pin-on gear P1, and the pin-on gear P2 rotatably, and is always connected to the input shaft 12. Since it comprises CR1 and a ring gear R1 that meshes with the pinion gear P2 and outputs a reduced speed rotation, it is possible to output a reduced speed rotation that reduces the input rotation of the input shaft 12 from the ring gear R1.
- the planetary gear unit PU includes a sun gear S2, a sun gear S3, a short pinion P3 that meshes with the sun gear S3, and a long pinion P4 that meshes with the sun gear S2 and meshes with the short peer P3, Since each of the planetary gear units PU is comprised of a radio gear type planetary gear unit PU having a carrier CR2 that rotatably supports the short pinion P3 and the long pinion P4 and a ring gear R3 that meshes with the long pinion P4. While it is possible to connect the rotating element and the output side member of each clutch or brake without complicating the members, the high rotating speed of each rotating element can be prevented and a good gear ratio can be obtained. be able to.
- the front By engaging the first clutch C-l and engaging the first brake B-l at the first forward speed, the second forward speed is established at the first clutch C-1 and the third clutch C-3. Are engaged with the third forward speed, and the first clutch C-1 and the fourth clutch C-4 are engaged with the fourth forward speed with the first clutch C-1 and the first clutch C-1.
- the vertical axis indicates the rotation speed of sun gear S2, sun gear S3, carrier CR2, and ring gear R3 of planetary gear unit PU
- the horizontal axis indicates the gears of sun gear S2, sun gear S3, carrier CR2, and ring gear R3.
- the sun gear S2 is positioned at the end of the lateral direction, and is configured correspondingly to the carrier CR2, the ring gear R3 connected to the counter gear 15, and the sun gear S3 in this order. Can do.
- FIG. 16 shows an automatic transmission 1 according to an eleventh embodiment.
- FIG. 16 a schematic configuration of the entire automatic transmission 1 according to the eleventh embodiment
- the automatic transmission 1 includes a transmission mechanism 2 in a mission case 3.
- a planetary gear unit PU is disposed on the input shaft 12, and the second clutch C 2 and the first clutch are arranged on the left side in the axial direction of the planetary gear unit PU in order from the left side.
- C 1, planetary gear DP, fourth clutch C 4 and third clutch C-3 are arranged.
- a counter gear 15 and a first brake B-1 are arranged on the right side in the axial direction of the planetary gear unit PU.
- a second brake B-2 is arranged on the outer peripheral side of the planetary gear unit PU.
- the left inner side of mission case 3 that is, planetary gear unit P On the left side of U, on the intermediate shaft 13, in order from the left side, the friction plate 3 1 of the second clutch C-2, the friction plate 21 of the first clutch C-1 and the third clutch C-3
- a friction plate 41 of the fourth clutch C-4 is disposed on the inner peripheral side of the friction plate 41 of the third clutch C3. Is arranged! /
- the transmission case 3 is connected to a boss 3b on the inner peripheral portion of the side wall 3a.
- the hydraulic servo 30 of the second clutch C-2 and the first clutch A C-1 hydraulic servo 20 is provided on the boss 3b.
- a planetary gear DP is disposed on the inner diameter side of the friction plate 21, and a hydraulic servo 50 for the fourth clutch C-4 is disposed adjacent to the right side of the planetary gear DP.
- a hydraulic servo 40 for the third clutch C-3 is disposed on the right side of the hydraulic servo 50 for the fourth clutch C-4.
- hydraulic servo 30, hydraulic servo 20, and planetary gear DP are arranged in order on boss portion 3b (the base side force of boss portion 3b is also directed to the right in the axial direction).
- the hydraulic servo 50 and the hydraulic servo 40 are disposed on the intermediate shaft 13.
- a flange-shaped support wall (center support member) 120 is fixedly disposed on the inner peripheral surface of the transmission case 3, and On the inner diameter side of the support wall 120, a counter gear 15 connected to a ring gear R3 of a planetary gear unit PU, which will be described later, via a ball bearing 121 is rotatably supported by the support wall 120! .
- the friction plate 71 of the second brake B-2 and the hydraulic servo 70 of the second brake B-2 are arranged on the outer peripheral side of the planetary gear unit PU.
- a counter gear 15 that is rotatably supported by the support wall 120 is disposed.
- the first brake B-1 The friction plate 61 and the hydraulic servo 60 of the first brake B-1 are disposed.
- the hydraulic servo 30 of the second clutch C-2 and the hydraulic servo 20 of the first clutch C-1 are arranged on the side opposite to the planetary gear set PU in the axial direction with respect to the planetary gear DP.
- the hydraulic servo 50 of the fourth clutch C-4 and the hydraulic servo 40 of the third clutch C-3 are arranged between the planetary gear DP and the planetary gear set PU in the axial direction.
- 5 and the hydraulic servo 60 of the first brake B-1 are arranged on the side opposite to the planetary gear DP in the axial direction with respect to the planetary gear unit PU.
- the planetary gear DP arranged inside the mission case 3 includes a sun gear S1, a carrier CR1, and a ring gear R1.
- the sun gear S1 is fixed to the boss portion 3b connected to the side wall portion 3a so as not to rotate.
- the carrier CR1 has two carrier plates in the left-right direction, and rotatably supports the pions PI, P2. These pinions PI and P2 are meshed with each other, and the former pinion P1 is meshed with the sun gear S1 and the latter pinion P2 is meshed with the ring gear R1.
- the right-side carrier plate is connected to the intermediate shaft 13, and the left-side carrier plate is connected to the clutch drum 32 that spline-engages the outer friction plate 31 of the second clutch C-2 friction plate 31. It is connected.
- the inner friction plate of the friction plate 21 of the first clutch C-1 is spline-engaged with the outer peripheral surface thereof.
- a hub member 113 is connected to the right side of the ring gear R1, and the inner friction plate of the friction plate 41 of the third clutch C-3 is spline engaged with the hub member 113.
- the first clutch C-1 includes a friction plate 21 and a hydraulic servo 20 that connects and disconnects the friction plate 21.
- the hydraulic servo 20 has a clutch drum 22, a piston member 23, a cancel plate 24, and a return spring 25, and these constitute an oil chamber 26 and a cancel oil chamber 27.
- the clutch drum 22 is disposed on the outer peripheral side of the inner diameter portion of the clutch drum 32 of the second clutch C-2, and the clutch drum 22 has an outer friction plate force S spline engagement of the friction plate 21 on the inner peripheral surface of the outer diameter portion.
- the tip of the outer diameter portion is connected to a transmission member 102 connected to a sun gear S3 of a planetary gear unit PU described later.
- the inner friction plate of the friction plate 21 is spline-engaged with the outer peripheral side of the ring gear R1.
- the piston member 23 is disposed on the right side of the clutch drum 22 so as to be movable in the axial direction, and forms a nectar-like oil chamber 26 between the seal rings a4 and a5 and the clutch drum 22. ing.
- Further cancel plate 24 Is prevented from moving rightward by the snap ring 29 fitted to the clutch drum 22 described above.
- the cancel plate 24 has a return spring 25 contracted between the piston member 23 arranged on the left side of the cancel plate 24 and a cancel-like cancel oil chamber 27 constituted by seal rings a4 and a6.
- the second clutch C2 is arranged on the left side of the first clutch C1, and is arranged on the boss portion 3b.
- the second clutch C-2 includes a friction plate 31 and a hydraulic servo 30 for connecting and disconnecting the friction plate 31.
- the hydraulic servo 30 includes a clutch drum 32, a piston member 33, a cancel plate 34, and a return spring 35, and these constitute an oil chamber 36 and a cancel oil chamber 37.
- the clutch drum 32 is connected to the carrier CR1 of the planetary gear DP at the right end of the inner diameter portion, and the hydraulic servo 20 of the first clutch C1 described above is disposed on the outer periphery of the clutch drum 32.
- the hydraulic servo 30 is included on the left side.
- the outer friction plate force of the friction plate 31 is engaged with the inner peripheral surface of the outer diameter portion of the clutch drum S by spline engagement, and the inner friction plate of the friction plate 31 is spline engagement with the hub member 112. .
- This hub member 112 passes through the outer periphery of the first clutch C-1, the planetary gear DP, the fourth clutch C-4, and the third clutch C-3, and is on the left side of the carrier CR2 of the planetary gear unit PU described later. It is connected to the transmission member 103 connected to the side plate (that is, the planetary gear DP side).
- the piston member 33 is disposed on the right side of the clutch drum 32 so as to be movable in the axial direction. ing.
- cancel plate 34 is prevented from moving rightward by the snap ring 39 fitted to the clutch drum 32 described above.
- the cancel plate 34 has a return spring 35 contracted between the piston member 33 arranged on the left side of the cancel plate 34 and a nectar-like cancel oil chamber 37 by the seal rings al and a3. .
- the clutch drum 32 of the second clutch C-2 is connected to the input shaft 12 via the intermediate shaft 13 and the carrier CR1, that is, rotates with the same input rotation as the input shaft 12. Therefore, an input rotation speed sensor for measuring the input rotation speed can be provided on the outer peripheral side of the clutch drum 32. For example, as compared with the case where the input rotation speed sensor is provided at a position where the rotation of the input shaft 12 can be directly measured. The input rotation speed sensor can be easily attached.
- the fourth clutch C-4 is arranged on the right side of the planetary gear unit PU and on the inner diameter side of the friction plate 41 of the third clutch C-3. And a hydraulic servo 50 for connecting and disconnecting the plate 51.
- the inner friction plate of the friction plate 51 is spline-engaged with the hub member 114, and the hub member 114 is connected to the sun gear S2 through the inner peripheral side of the hydraulic servo 40 of the third clutch C3.
- the outer friction plate of the friction plate 51 is splined to the inner peripheral side of the clutch drum 52.
- the clutch drum 52 shares the right side plate of the carrier CR1 and the inner peripheral side is the intermediate shaft 13. It is connected to.
- the intermediate shaft 13 is spline-engaged with the aforementioned input shaft 12, that is, the clutch drum 52 is connected to the input shaft 12 via the intermediate shaft 13.
- the fourth clutch C-4 enables the direct input shaft 12 (intermediate shaft 13) and the sun gear S2 to be engaged and disengaged through the carrier CR1 of the planetary gear DP, for example.
- the hydraulic servo 50 has a clutch drum 52, a piston member 53, a cancel plate 54, and a return spring 55, and these constitute an oil chamber 56 and a cancel oil chamber 57.
- the clutch drum 52 has the inner peripheral side attached to the intermediate shaft 13 and a part of the outer peripheral surface of the intermediate shaft 13 is also used as a clutch drum. A part of the outer peripheral surface of 13 and the clutch drum 52 form a clutch drum as the hydraulic servo 50.
- the piston member 53 is disposed on the clutch drum 52 so as to be movable in the axial direction, and a seal-like oil chamber 56 is formed between the piston member 53 and the clutch drum 52 by the seal rings a7 and a8.
- the piston member 53 has an outer peripheral part facing the front surface of the friction plate 51. Further, the cancel plate 54 is prevented from moving to the right side by the snap ring 59 fitted to the outer peripheral surface on the inner diameter side of the clutch drum 52, and the cancel plate 54 is connected to the piston member 53 disposed on the left side thereof. In between, the return spring 55 is contracted and the nail-like cancel oil chamber 57 is constituted by the seal rings a7 and a9.
- the third clutch C-3 is located on the right side of the fourth clutch C-4, and is disposed on the intermediate shaft 13 via the transmission member 101.
- a hydraulic servo 40 for connecting and disconnecting the plate 41 is provided.
- the inner friction plate of the friction plate 41 is spline-engaged with the outer peripheral surface of the hub member 113 connected to the ring gear R1. Further, the outer friction plate of the friction plate 41 is spline-engaged with an inner peripheral side of a clutch drum 42 described later, and the clutch drum 42 is It is connected to the transmission member 101 connected to the sun gear S2 of the planetary gear unit PU.
- the hydraulic servo 40 includes a clutch drum 42, a piston member 43, a cancel plate 44, and a return spring 45, and these constitute an oil chamber 46 and a cancel oil chamber 47.
- the clutch drum 42 is attached to the transmission member 101 on the inner peripheral side, and a part of the outer peripheral surface of the transmission member 101 is shared as the clutch drum.
- a clutch drum as a hydraulic servo 40 is formed by a part and the clutch drum 42.
- the piston member 43 is disposed on the clutch drum 42 so as to be movable in the axial direction, and an oily chamber 46 is formed between the piston member 43 and the clutch drum 42 by the seal rings alO, all.
- the piston member 43 has the outer peripheral portion opposed to the front surface of the friction plate 41.
- cancel plate 44 is prevented from moving to the left side by a snap ring 49 fitted to the outer peripheral surface of the transmission member 101, and between the piston member 43 disposed on the right side thereof, The return spring 45 is contracted and the nail-like cancel oil chamber 47 is constituted by the seal rings alO and al2.
- Second brake B-2 is arranged on the outer diameter side of ring gear R3 of planetary gear unit PU.
- the second brake B-2 includes a friction plate 71 and a hydraulic servo 70 for connecting and disconnecting the friction plate 71.
- the outer friction plate of the friction plate 71 is spline-engaged with the inner peripheral surface of the transmission case 3, and the inner friction plate is connected to the transmission member 103 described above (that is, to the carrier CR2 of the planetary gear unit PU). It is splined to the hub member 117 (connected).
- the hydraulic servo 70 includes a cylinder member 72, a piston member 73, a cancel plate 74, and a return spring 75.
- An oil chamber 76 is formed between the cylinder member 72 and the piston member 73. Yes.
- the piston member 73 is arranged so as to be movable in the axial direction, and the left side end portion faces the friction plate 71.
- An oil chamber 76 is formed between the piston member 73 and the transmission case 3 by two seal rings al5 and al6. Further, the cancel plate 74 is prevented from moving to the left by a snap ring 79 fitted to the inner peripheral surface of the mission case 3.
- the first brake B-1 is connected to the right side of the transmission case 3 from the transmission case 3 And a partition wall member 3c separating the housing case (not shown).
- the first brake B-1 includes a friction plate 61 and a hydraulic servo 60 that connects and disconnects the friction plate 61.
- the outer friction plate of the friction plate 61 is splined to the inner peripheral surface of the transmission case 3, and the inner friction plate is connected to a knob member 116 connected to the sun gear S2 of the planetary gear unit PU via the transmission member 104. The spline is engaged.
- the hydraulic servo 60 includes a piston member 63, a cancel plate 64, and a return spring 65, and an oil chamber 66 is formed between the piston member 63 and the cylinder portion formed in the partition wall member 3c. .
- the piston member 63 is disposed so as to be movable in the axial direction, and the left side end portion faces the friction plate 61.
- An oil chamber 66 is formed between the piston member 63 and the partition wall member 3c by two seal rings al3 and al4. Further, the cancel plate 64 is prevented from moving leftward by a snap ring 69 fitted to the partition wall member 3c.
- the planetary gear unit PU is composed of a sun gear S2, a sun gear S3, a short pinion P3 meshed with the sun gear S3, a long pinion P4 meshed with the sun gear S2 and the short pinion P3, and these short beons. Consists of a loose Ravio-type planetary gear that has a carrier CR2 that supports P3 and the long pion P4 by itself on both sides, and a ring gear R3 that meshes with the long pion P4! RU
- a transmission member 104 passing through the inner peripheral side of the counter gear 15 is connected to the right side, and the hub member 116 of the first brake B-1 is connected via the transmission member 104. It is connected.
- the sun gear S2 is connected to the transmission member 101 on the left side, and the hub member 114 of the fourth clutch C-4 and the clutch drum 42 of the third clutch C-3 are connected via the transmission member 101. It is connected to.
- the transmission member 102 is connected to the left side, and the clutch drum 22 of the first clutch C-1 is connected through the connection member 102.
- the left side that is, the side plate on the planetary gear DP side
- the carrier CR2 is connected to the transmission member 103, and is connected to the hub member 112 of the second clutch C-2 via the transmission member 103.
- the carrier CR2 is coupled to the hub member 117 of the second brake B-2 via the transmission member 103.
- the ring gear R3 is connected to the counter gear via the transmission member 105.
- 15 is connected.
- the counter gear 15 is engaged with the large-diameter gear 82 connected to the counter shaft 81 as described above, and the left and right axles 931, 93r (that is, the counter gear 15 via the counter shaft portion 80, the differential gear portion 90, etc.) Drive wheel).
- each oil passage configuration and supply of hydraulic oil will be briefly described.
- the oil chamber 36 of the hydraulic servo 30 of the second clutch C 2 that is, the oil chamber 36 formed by sealing between the clutch drum 32 and the piston member 33 with the seal ring al, a2, is provided with the clutch drum 32 and the boss.
- the oil passage c30 in the boss portion 3b communicates with the seal ring dl, d2 between the portion 3b and hydraulic oil is supplied from the oil passage c30.
- oil is also supplied to a cancel oil chamber 37 (not shown) that is configured to be sealed between the piston member 33 and the cancel plate 34 by seal rings al and a3.
- the oil chamber 26 of the hydraulic servo 20 of the first clutch C-1 that is, the oil chamber 26 constituted by sealing the gap between the clutch drum 22 and the piston member 23 with seal rings a4 and a5
- the second clutch C-2 has a seal ring d3, d4 between the clutch drum 32 and the boss 3b, and a seal ring d5, d6 between the clutch drum 32 and the clutch drum 22.
- the oil passage c20 in the boss portion 3b is communicated with the seal, and hydraulic oil is supplied from the oil passage c20. Note that oil is supplied from an oil passage (not shown) to a cancel oil chamber 27 that is configured to be sealed between the piston member 23 and the cancel plate 24 by seal rings a4 and a6.
- the oil chamber 56 of the hydraulic servo 50 of the fourth clutch C-4 that is, the oil chamber 56 formed by sealing between the clutch drum 52 and the piston member 53 by seal rings a7 and a8,
- the oil passage c50 in the boss portion 3b is sealed between the boss portion 3b and the intermediate shaft 13 by the seal ring d9, dlO, the oil passage c51 in the intermediate shaft 13, the axial oil passage not shown, and
- the fluid is communicated via an oil passage c53, and hydraulic oil is supplied from the oil passage c53.
- oil is also supplied to a cancel oil chamber 57 (not shown) that is configured by sealing between the piston member 53 and the cancel plate 54 by seal rings a7 and a9.
- the oil chamber 46 of the hydraulic servo 40 of the third clutch C 3 that is, the oil chamber 46 configured by sealing between the clutch drum 42 and the piston member 43 by seal rings alO, all.
- the seal ring d7, d8 is provided between the boss 3b and the intermediate shaft 13, and the intermediate shaft 13 and the transmission member 101 (I.e., the clutch drum) is sealed with seal rings dl l and dl2, respectively, and the oil passage c40 in the boss 3b communicates with the oil passages c41, c42, and c43 in the intermediate shaft 13, Hydraulic fluid is supplied from the oil passage c43.
- an oil passage force oil (not shown) is supplied to a cancel oil chamber 47 configured to be sealed between the piston member 43 and the cancel plate 44 by seal rings alO and al2.
- the oil chamber 66 of the hydraulic servo 60 of the first brake B-1 that is, the oil constituted by sealing the space between the partition member 3c of the transmission case 3 and the piston member 63 by seal rings al3, al4.
- the chamber 66 is supplied with oil passage force hydraulic oil of the partition member 3c (not shown).
- the oil chamber 76 of the hydraulic servo 70 of the second brake B-2 that is, the oil chamber 76 formed by sealing between the cylinder member 72 and the piston member 73 by seal rings al5 and al6,
- the oil passage force hydraulic oil in the transmission case 3 (not shown) is supplied.
- the input shaft 12 and the intermediate shaft 13 are formed with an oil passage c80 in the axial direction, and the oil passage c80 is also filled with lubricating oil (not shown) in the boss portion 3b. Supplied.
- the input shaft 12 and the intermediate shaft 13 are provided with a plurality of holes (not shown) from the oil passage 80 in the radial direction, and the lubricating oil supplied to the oil passage c80 is scattered from these holes.
- an oil passage c90 is formed in the input shaft 12 in the axial direction.
- the oil passage 90 communicates with the lockup clutch 10 via an oil passage (not shown), and the oil passage c90 is connected to a hydraulic control device force (not shown) via an oil passage (not shown) in the partition wall member 3c.
- the hydraulic oil is supplied, the hydraulic oil is supplied to the friction plate of the lock-up clutch 10 and presses the friction plate to engage the lock-up clutch 10.
- the fourth clutch C-4 is connected to the input shaft 12 and the sun gear.
- the second clutch C-2 is placed on the transmission path that connects between the carrier CR1 and the carrier CR2, and the second clutch C-2 is placed on the transmission path that connects the carrier S2. Since the output transmission member 103 of the two clutch C-2 is connected to the carrier CR2 on the planetary gear DP in the axial direction of the planetary gear unit PU, a member for enclosing the planetary gear unit PU can be eliminated. As a result, the radial direction of the vehicle automatic transmission 1
- each clutch it is possible to arrange the support wall 120 and supply the hydraulic fluid of the clutch from the support wall 120, so that the number of seal rings can be reduced. As a result, the sliding resistance of the seal ring can be reduced, and the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- the carrier CR1 and the fourth clutch C—4 A part of the members constituting the clutch drum 52 of the hydraulic servo 50 (that is, the clutch drum 52 and the side plate of the carrier CR1) can be shared, so that a reduction in size and weight can be achieved.
- the hydraulic servo 30 of the second clutch C-2 is disposed on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, the hydraulic servo 30 of the second clutch C-2 is connected to the hydraulic servo 30 of the case 4. It is possible to supply oil passage force hydraulic oil provided in the boss 3b connected to one end. As a result, the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. Improving power transmission efficiency as automatic transmission 1
- the hydraulic servo 40 of the third clutch C 3 is arranged between the planetary gear unit PU and the planetary gear DP in the axial direction, the planetary gear PU is opposite to the planetary gear PU with respect to the planetary gear DP.
- the output of the third clutch C-3 which can shorten the distance between the third clutch C-3 and the planetary gear unit PU and requires strength to transmit high torque,
- the side transmission member can be shortened. As a result, the weight can be reduced, and the controllability can be improved as the vehicle automatic transmission 1.
- the hydraulic servo 20 of the first clutch C-1 is disposed on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, the hydraulic servo 20 of the first clutch C-1 is Oil path force provided in the boss 3b connected to one end Supply hydraulic fluid And can be made possible.
- the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. Improving power transmission efficiency as automatic transmission 1
- the first brake B-1 that can freely lock the rotation of the sun gear S2 with respect to the case 4 is provided, and the hydraulic servo 60 of the first brake B-1 is connected to the counter gear 15 with the planetary gear unit PU. Since the locking force transmission member of the first brake B-1 is connected to the sun gear S2 through the inner peripheral side of the counter gear 15, the locking force transmission member of the first brake B-1 is arranged on the opposite side in the axial direction. And the sun gear S2 can be connected without complicating the members, and the vehicle automatic transmission 1 can be made compact.
- the output-side transmission member 103 is connected to the carrier CR2 through the outer peripheral side of the output-side transmission members 101, 102 of the third and first clutches C-3, C-1, and the fourth clutch C-4. And the transmission member 101 on the output side of the third clutch C-3 is connected to the sun gear S2 and transmits on the output side of the fourth clutch C-4 and the third clutch C-3 that rotate integrally. Since the member 101 and the sun gear S2 are arranged on the inner peripheral side with respect to the transmission member 102 on the output side of the first clutch C-1, the rotation speed is higher than that of the transmission member 103 on the output side of the second clutch C-2.
- the transmission member 101 on the output side of the fourth clutch C—4 is the output transmission member 102 on the output side of the first clutch C—1 on the inner peripheral side of the transmission member 103 on the output side of the second clutch C-2.
- the diameter of the transmission member 101 on the output side of the fourth clutch C-4 is set to the transmission member 103 on the output side of the second clutch C-2. And can be made smaller than the diameter, it is possible to reduce the weight I spoon than when disposed on the outer peripheral side.
- inertia inertial force
- the third and first clutches C-3, C-1 are arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the outputs of the third and first clutches C-3, C-1 are also provided.
- Side transmission members 101 and 102 are connected to the sun gear S2 and sun gear S3, respectively, and the fourth clutch C-4 is arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the output side of the fourth clutch C-4
- the transmission member 101 is connected to the sun gear S2, and the second clutch C— 2 is arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the transmission member 103 on the output side of the second clutch C-2 is connected to the output side of the third and first clutches C-3 and C-1.
- the transmission member on the output side of the fourth clutch C-4 which is faster than the transmission member 103 on the output side of the second clutch C-2. Since 101 is on the inner circumferential side, the diameter of the transmission member 101 on the output side of the fourth clutch C 4 can be made smaller than the diameter of the transmission member 103 on the output side of the second clutch C-2. It is possible to achieve a lighter weight than the case of using. In addition, inertia (inertial force) can be reduced compared to the case of the outer peripheral side, so that the automatic transmission 1 for vehicles is more controllable.
- the transmission member on the input side of the fourth clutch C-4 it is directly connected to the carrier CR1, and together with a part of the carrier CR1, it is configured as a part of the hydraulic servo 50 of the fourth clutch C-4.
- Part of the components that make up the carrier CR1 and the hydraulic servo 50 of the fourth clutch C-4 can be shared. You can make a habit.
- the hub member 111 of the first clutch C-1 is connected to the ring gear R1
- the output transmission member 102 of the first clutch C-1 is connected to the sun gear S3
- the first clutch C- A part of the transmission member 102 on the output side of 1 is configured as a clutch drum 22 of the hydraulic servo 20 of the first clutch C—1
- the hydraulic servo 20 is configured as the hydraulic pressure of the planetary gear DP and the second clutch C—1. Since it is arranged on the boss part 3b between the servo 20 and the axial direction, it is connected to the hydraulic servo 20 of the first clutch C-1 from the oil passage c20 provided in the boss part 3b connected to the side wall 3a of the case 4. It may be possible to supply hydraulic oil.
- the hydraulic servo 20 of the first clutch C-1 is disposed on the input shaft 12 away from the boss 3b, and hydraulic oil is supplied through the oil passage in the input shaft 12.
- the length of the oil passage can be shortened by not interposing the oil passage in the input shaft 12.
- the counter gear 15 connected to the ring gear R3 of the planetary gear unit PU is provided.
- the counter gear 15 is disposed on the opposite side to the planetary gear DP in the axial direction with respect to the planetary gear unit PU, and the second brake B-2 Is a multi-plate brake composed of a plurality of friction plates 71, and the multi-plate brake is disposed on the outer peripheral side of the planetary gear unit PU.
- the counter gear 15 is connected between the planetary gear unit PU and the planetary gear DP.
- the hub member 117 of the second brake B-2 can be shared with the carrier CR2 in common with the output member 103 on the output side of the second clutch C-2, compared with Compared to the case where a band brake is installed on the outer peripheral side of the transmission member 103 on the output side of the clutch C-2, multiple plates are provided in the outer peripheral side space of the planetary gear unit PU. Allows you to place the brakes, while maintaining a compact I spoon, the brake can be Taiti spoon.
- the counter shaft 81 is arranged in parallel to the input shaft 12 and connected via the counter gear 15 connected to the ring gear R3.
- the counter gear 15 is disposed on the opposite side to the planetary gear DP in the axial direction with respect to the planetary gear unit PU, and is supported by the support portion 120a connected to the support wall 120 extending from the case 4.
- the distance between the planetary gear DP and the planetary gear unit PU can be shortened, and the output side member 101 of the third clutch C-3 and the output side of the first clutch C-1 that need strength in particular to transmit high torque
- the member 102 can be shortened. This makes it possible to reduce the weight and improve the controllability of the vehicle automatic transmission 1.
- the carrier CR1 is connected to the input shaft 12 on the planetary gear unit PU side with respect to the planetary gear DP, and the second clutch C is connected to the planetary gear DP on the side opposite to the planetary gear unit PU in the axial direction.
- the clutch drum 32 Since it is connected to the clutch drum 32, which is the transmission member on the input side of 2, the transmission member 32 on the input side of the carrier CR1 and the second clutch C 2 and the input shaft 12 can be connected without complicating the members.
- the vehicle automatic transmission 1 is the vehicle automatic transmission 1
- the hub member 116 of the first brake B-1 and the transmission member 104 connected thereto are connected to the sun gear S2 on the opposite side of the planetary gear DP in the planetary gear unit PU in the axial direction.
- the hub member 116 and the transmission member 104 of the brake B-1 and the sun gear S2 can be connected without complicating the members, and the automatic transmission 1 for the vehicle can be connected.
- the planetary gear DP is a carrier that supports the sun gear S1 whose rotation is always fixed with respect to the case 4, the pin-on gear P1, and the pin-on gear P2 rotatably, and is always connected to the input shaft 12. Since it comprises CR1 and a ring gear R1 that meshes with the pinion gear P2 and outputs a reduced speed rotation, it is possible to output a reduced speed rotation that reduces the input rotation of the input shaft 12 from the ring gear R1.
- the planetary gear unit PU includes a sun gear S2, a sun gear S3, a short pinion P3 that meshes with the sun gear S3, a long pinion P4 that meshes with the sun gear S2, and meshes with the short peer P3, It consists of a radio gear type planetary gear unit PU having a carrier CR2 that rotatably supports the short pinion P3 and the long pinion P4, and a ring gear R3 that meshes with the long pinion P4. While it is possible to connect the rotating element and the output side member of each clutch or brake without complicating the members, the high rotating speed of each rotating element can be prevented and a good gear ratio can be obtained. be able to.
- the first clutch C-1 is engaged and the second brake B-2 is locked to engage the first forward speed, and the first clutch C-1 is engaged and the first brake By engaging B-1, the second forward speed is established. By engaging the first clutch C-1 and the third clutch C-3, the third forward speed is established, and the first clutch C-1 is engaged. And the 4th clutch C—4.
- Engaging the 6th forward speed By engaging the 6th forward speed, the second clutch C-2 and the third clutch C-3 are engaged, the 7th forward speed is engaged, the second clutch C-2 is engaged, and the first brake B -Locking 1 to move forward 8th gear, engaging 3rd clutch C-3 or 4 clutch C-4 and locking 2nd brake B-2 Each can be achieved.
- the vertical axis indicates the rotational speeds of the sun gear S2, sun gear S3, carrier CR2, and ring gear R3 of the planetary gear unit PU
- the horizontal axis indicates the gears of the sun gear S2, sun gear S3, carrier CR2, and ring gear R3.
- the sun gear S2 is positioned at the end of the lateral direction, and is configured correspondingly to the carrier CR2, the ring gear R3 connected to the counter gear 15, and the sun gear S3 in this order. Can do.
- vehicle automatic transmission 1 according to the eleventh embodiment is configured so that the speed change mechanism 2 is
- the vehicle automatic transmission 1 By reversing substantially in the 11 11 direction (axial direction), the vehicle automatic transmission 1 according to a thirteenth embodiment described later can be configured.
- FIG. 17 is a cross section showing an automatic transmission 1 according to a twelfth embodiment.
- the automatic transmission 1 according to the twelfth embodiment includes an automatic transmission according to the eleventh embodiment.
- the hydraulic servo 50 of the 4th clutch C-4 is applied to the planetary gear unit PU.
- the planetary gear unit PU is repositioned on the opposite side in the axial direction. Specifically, the hydraulic servo 50 of the 4th clutch C-4 is placed adjacent to the support wall 120 on the right side of the counter gear 15, and the inside of the partition member 3c It is arranged on the boss 3d connected to the peripheral side.
- the hydraulic servo 20 of C 1 is arranged on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, and the hydraulic servo 40 of the third clutch C 3 is connected to the planetary gear DP.
- the planetary gear unit PU is arranged in the axial direction. Is arranged on the opposite side in the axial direction.
- the fourth clutch C-4 is connected to the input shaft 12 and the sun gear.
- the second clutch C-2 is placed on the transmission path that connects between the carrier CR1 and the carrier CR2, and the second clutch C-2 is placed on the transmission path that connects the carrier S2. Since the output transmission member 103 of the two clutch C-2 is connected to the carrier CR2 on the planetary gear DP in the axial direction of the planetary gear unit PU, a member for enclosing the planetary gear unit PU can be eliminated. As a result, the radial direction of the vehicle automatic transmission 1
- the transmission member that requires high rigidity can be shortened, the weight can be reduced, and the controllability of the vehicle automatic transmission 1 can be improved.
- each clutch it is possible to arrange the support wall 120 and supply the hydraulic fluid of the clutch from the support wall 120, so that the number of seal rings can be reduced. As a result, the sliding resistance of the seal ring can be reduced, and the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- the hydraulic servo 30 of the second clutch C-2 is arranged on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, the hydraulic servo 30 of the second clutch C-2 is connected to the hydraulic servo 30 of the case 4. It is possible to supply oil passage force hydraulic oil provided in the boss 3b connected to one end. As a result, the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. Improving power transmission efficiency as automatic transmission 1
- the friction plate 51 of the fourth clutch C 4 is relatively on the outer peripheral side. Since the area of the friction plates 51 can be increased, a torque capacity that can be transmitted can be secured, and the number of friction plates 51 can be reduced. You can also. Further, the hydraulic oil provided in the boss portion 3d connected to one end of the case 4 can be supplied to the hydraulic servo 50 of the fourth clutch C-4. As a result, the oil passage power provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal ring as compared with the case of supplying hydraulic oil. The power transmission efficiency of the automatic transmission 1 can be improved.
- the hydraulic servo 40 of the third clutch C 3 is arranged between the planetary gear unit PU and the planetary gear DP in the axial direction, the planetary gear PU is opposite to the planetary gear PU in the axial direction with respect to the planetary gear DP.
- the output of the third clutch C-3 which can shorten the distance between the third clutch C-3 and the planetary gear unit PU and requires strength to transmit high torque,
- the side transmission member 101 can be shortened. As a result, it is possible to reduce the weight and improve the controllability of the vehicle automatic transmission 1.
- the hydraulic servo 20 of the first clutch C-1 is arranged on the opposite side of the planetary gear unit PU in the axial direction with respect to the planetary gear DP, the hydraulic servo 20 of the first clutch C-1 is It is possible to supply oil passage force hydraulic oil provided in the boss 3b connected to one end. As a result, the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. Improving power transmission efficiency as automatic transmission 1
- the first brake B-1 that can freely lock the rotation of the sun gear S2 with respect to the case 4 is provided, and the hydraulic servo 60 of the first brake B-1 is connected to the counter gear 15 with the planetary gear unit PU. Since the locking force transmission member of the first brake B-1 is connected to the sun gear S2 through the inner peripheral side of the counter gear 15, the locking force transmission member of the first brake B-1 is arranged on the opposite side in the axial direction. And the sun gear S2 can be connected without complicating the members, and the vehicle automatic transmission 1 can be made compact.
- the output-side transmission member 103 is connected to the carrier CR2 through the outer peripheral side of the output-side transmission members 101, 102 of the third and first clutches C-3, C-1, and is connected to the fourth clutch C-4.
- Output side The transmission member 104 of the third clutch C-3 and the transmission member 101 on the output side of the third clutch C-3 are connected to the sun gear S2, and the transmission member 104 and the third clutch of the output side of the fourth clutch C 4 that rotate integrally therewith.
- the output side of the second clutch C-2 The first clutch C 1 is located on the inner peripheral side of the output member 103 of the output side of the second clutch C-2.
- the diameter of the transmission member 104 on the output side of the fourth clutch C-4 is made smaller than the diameter of the transmission member 103 on the output side of the second clutch C-2. This makes it possible to achieve a lighter weight than when it is arranged on the outer peripheral side.
- inertia inertial force
- the hub member 111 of the first clutch C-1 is connected to the ring gear R1
- the output transmission member 102 of the first clutch C-1 is connected to the sun gear S3
- the first clutch C- A part of the output member 102 on the output side of 1 is configured as a clutch drum 22 of the hydraulic servo 20 of the first clutch C—1
- the hydraulic servo 20 is composed of the planetary gear DP and the hydraulic servo 20 of the second clutch C—1.
- the first clutch C-1 Compared to the case where the hydraulic servo 20 is disposed on the input shaft 12 away from the boss portion 3b and hydraulic oil is supplied through the oil passage in the input shaft 12, the oil passage in the input shaft 12 is not interposed.
- the oil path length can be shortened and the controllability of the vehicle automatic transmission 1 can be improved.
- the counter gear 15 is connected to the ring gear R3 of the planetary gear unit PU.
- the counter gear 15 is arranged on the opposite side of the planetary gear DP in the axial direction with respect to the planetary gear unit PU, and the second brake B-2 Is a multi-plate brake composed of a plurality of friction plates 71, and the multi-plate brake is disposed on the outer peripheral side of the planetary gear unit PU.
- the counter gear 15 is connected between the planetary gear unit PU and the planetary gear DP.
- the hub member 117 of the second brake B-2 can be shared with the carrier CR2 in common with the output member 103 on the output side of the second clutch C-2, compared with Compared to the case where a band brake is installed on the outer peripheral side of the transmission member 103 on the output side of the clutch C-2, multiple plates are provided in the outer peripheral side space of the planetary gear unit PU. Allows you to place the brakes, while maintaining a compact I spoon, the brake can be Taiti spoon.
- a counter shaft 81 arranged parallel to the input shaft 12 and connected via a counter gear 15 connected to the ring gear R3 is provided, and the output rotation from the ring gear R3 1S via the counter gear 15 Since it is transmitted to the countershaft 81, the vehicle automatic transmission 1 can be suitably used for an FF type vehicle.
- the counter gear 15 is disposed on the opposite side to the planetary gear DP in the axial direction with respect to the planetary gear unit PU, and is supported by the support portion 120a connected to the support wall 120 extending from the case 4.
- the distance between the planetary gear DP and the planetary gear unit PU can be shortened, and the output side member 101 of the third clutch C-3 and the output side of the first clutch C-1 that need strength in particular to transmit high torque
- the member 102 can be shortened. This makes it possible to reduce the weight and improve the controllability of the vehicle automatic transmission 1.
- the carrier CR1 is connected to the input shaft 12 on the planetary gear unit PU side with respect to the planetary gear DP, and the second clutch C is connected to the planetary gear DP on the side opposite to the planetary gear unit PU in the axial direction.
- Clutch drum as a transmission member on the input side of 2 32, the transmission member 32 on the input side of the carrier CR1 and the second clutch C2 and the input shaft 12 can be connected without complicating the members, and the vehicle automatic transmission 1 can be connected.
- the planetary gear DP supports a sun gear S1 whose rotation is always fixed with respect to the case 4, a pin-on gear P1 and a pin-on gear P2, and a carrier that is always connected to the input shaft 12. Since it comprises CR1 and a ring gear R1 that meshes with the pinion gear P2 and outputs a reduced speed rotation, it is possible to output a reduced speed rotation that reduces the input rotation of the input shaft 12 from the ring gear R1.
- the planetary gear unit PU includes a sun gear S2, a sun gear S3, a short pinion P3 that meshes with the sun gear S3, a long pinion P4 that meshes with the sun gear S2, and meshes with the short peer P3, It consists of a radio gear type planetary gear unit PU having a carrier CR2 that rotatably supports the short pinion P3 and the long pinion P4, and a ring gear R3 that meshes with the long pinion P4. While it is possible to connect the rotating element and the output side member of each clutch or brake without complicating the members, the high rotating speed of each rotating element can be prevented and a good gear ratio can be obtained. be able to.
- first clutch C-1 is engaged and the second brake B-2 is locked to engage the first forward speed
- first clutch C-1 is engaged and the first brake
- second forward speed is established.
- the third forward speed is established, and the first clutch C-1 is engaged.
- the fourth clutch C-4 are engaged with the fourth forward speed, and the first clutch C-1 and the second clutch C-2 are engaged with the fifth forward speed.
- the vertical axis indicates the rotation speed of sun gear S2, sun gear S3, carrier CR2, and ring gear R3 of planetary gear unit PU
- the horizontal axis indicates the gears of sun gear S2, sun gear S3, carrier CR2, and ring gear R3.
- the sun gear S2 is positioned at the end of the lateral direction, and is configured correspondingly to the carrier CR2, the ring gear R3 connected to the counter gear 15, and the sun gear S3 in this order. Can do.
- FIG. 18 is a cross section showing an automatic transmission 1 according to a thirteenth embodiment.
- FIG. 13 is a diagram. Note that, in the thirteenth embodiment described below, parts having the same configuration as that of the automatic transmission 1 according to the eleventh embodiment are denoted by the same reference numerals, and the description thereof will be simplified.
- the automatic transmission 1 according to the thirteenth embodiment includes an automatic transmission according to the eleventh embodiment.
- the transmission mechanism 2 is configured by being substantially reversed in the right direction (axial direction).
- the hydraulic servo 20 of C 1 is arranged on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, and the hydraulic servo 50 of the fourth clutch C 4 and the hydraulic servo 40 of the third clutch C 3 are connected to the planetary gear DP. It is arranged between the planetary gear unit PU and the counter gear 15 and the hydraulic servo 60 of the first brake B-1 is arranged on the opposite side of the planetary gear DP with respect to the planetary gear PU. ing.
- the fourth clutch C-4 is connected to the input shaft 12 and
- the second clutch C-2 is placed on the transmission path that connects the Arrange the output transmission member 103 of the second clutch C-2 in the axial direction on the planetary gear DP on the planetary gear unit PU. Since it is connected to CR2, it is possible to eliminate the need to wrap the planetary gear unit PU. As a result, the radial direction of the vehicle automatic transmission 1
- the transmission member that requires high rigidity can be shortened, the weight can be reduced, and the controllability of the vehicle automatic transmission 1 can be improved.
- each clutch it is possible to arrange the support wall 120 and supply the hydraulic fluid of the clutch from the support wall 120, so that the number of seal rings can be reduced. As a result, the sliding resistance of the seal ring can be reduced, and the power transmission efficiency of the vehicle automatic transmission 1 can be improved.
- the hydraulic servo 50 of the fourth clutch C 4 is disposed adjacent to the planetary gear DP between the planetary gear unit PU and the planetary gear DP, so that the carrier CR1 and the fourth clutch C-4 have A part of the members constituting the clutch drum 52 of the hydraulic servo 50 (that is, the clutch drum 52 and the side plate of the carrier CR1) can be shared, so that a reduction in size and weight can be achieved.
- the hydraulic servo 30 of the second clutch C-2 is disposed on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, the hydraulic servo 30 of the second clutch C-2 is connected to the hydraulic servo 30 of the case 4. It is possible to supply oil passage force hydraulic oil provided in the boss 3b connected to one end. As a result, the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. Improving power transmission efficiency as automatic transmission 1
- the hydraulic servo 40 of the third clutch C 3 is arranged between the planetary gear unit PU and the planetary gear DP in the axial direction, the planetary gear PU is opposite to the planetary gear PU with respect to the planetary gear DP.
- the distance between the third clutch C-3 and the planetary gear unit PU can be shortened compared to the case where it is installed in the center, and the strength is necessary to transmit high torque.
- the required output side transmission member of the third clutch C-3 can be shortened. As a result, it is possible to reduce the weight and improve the controllability of the vehicle automatic transmission 1.
- the hydraulic servo 20 of the first clutch C-1 is arranged on the opposite side of the planetary gear unit PU with respect to the planetary gear DP, the hydraulic servo 20 of the first clutch C-1 is It is possible to supply oil passage force hydraulic oil provided in the boss 3b connected to one end. As a result, the oil passage cover provided in the input shaft 12 can also reduce the number of seal rings and reduce the sliding resistance of the seal rings as compared with the case of supplying hydraulic oil. Improving power transmission efficiency as automatic transmission 1
- the first brake B-1 that can freely lock the rotation of the sun gear S2 with respect to the case 4 is provided, and the hydraulic servo 60 of the first brake B-1 is connected to the counter gear 15 with the planetary gear unit PU. Since the locking force transmission member of the first brake B-1 is connected to the sun gear S2 through the inner peripheral side of the counter gear 15, the locking force transmission member of the first brake B-1 is arranged on the opposite side in the axial direction. And the sun gear S2 can be connected without complicating the members, and the vehicle automatic transmission 1 can be made compact.
- the output-side transmission member 103 is connected to the carrier CR2 through the outer peripheral side of the output-side transmission members 101, 102 of the third and first clutches C-3, C-1, and the fourth clutch C-4.
- the output shaft of the intermediate shaft 13 and the output clutch 101 of the output of the third clutch C-3 are connected to the sun gear S2 and the output of the fourth clutch C-4 that rotates integrally therewith.
- the intermediate shaft 13, which is the transmission member on the side, the transmission member 101 on the output side of the third clutch C-3, and the sun gear S2 are located on the inner peripheral side with respect to the transmission member 102 on the output side of the first clutch C-1.
- the diameter of the intermediate shaft 13, which is the transmission member on the output side of 4 can be made smaller than the diameter of the transmission member 103 on the output side of the second clutch C—2, and is lighter than when it is arranged on the outer peripheral side. The amount can be reduced.
- inertia inertial force
- the third and first clutches C-3, C-1 are arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the outputs of the third and first clutches C-3, C-1 are provided.
- Side transmission members 101 and 102 are connected to the sun gear S2 and sun gear S3, respectively, and the fourth clutch C-4 is arranged on the planetary gear DP side with respect to the planetary gear unit PU, and the output side of the fourth clutch C-4
- the intermediate shaft 13 which is the transmission member of the second clutch C2 is connected to the sun gear S2, the second clutch C2 is disposed on the planetary gear DP side with respect to the planetary gear unit PU, and the transmission member 103 on the output side of the second clutch C-2 is provided.
- the output side transmission member 103 of the second clutch C-2 is connected. 4th clutch C— Since the intermediate shaft 13 that is the output member of the output side 4 is the inner peripheral side, the diameter of the intermediate shaft 13 that is the output member of the fourth clutch C 4 is set to the The diameter of the transmission member 103 can be made smaller than that of the transmission member 103, and the weight can be reduced compared to the case of the outer peripheral side. In addition, since inertia (inertia force) can be reduced compared to the case of the outer peripheral side, the controllability of the vehicle automatic transmission 1 can be improved.
- the transmission member on the input side of the fourth clutch C-4 it is directly connected to the carrier CR1, and is configured as a part of the hydraulic servo 50 of the fourth clutch C-4 with a part of the carrier CR1.
- Part of the components that make up the carrier CR1 and the hydraulic servo 50 of the fourth clutch C-4 can be shared. You can make a habit.
- the hydraulic servo 30 of the second clutch C-2 is moved away from the boss 3b.
- the oil passage length can be shortened.
- controllability can be improved.
- the hub member 111 of the first clutch C-1 is connected to the ring gear R1
- the output transmission member 102 of the first clutch C-1 is connected to the sun gear S3
- the first clutch C- A part of the output member 102 on the output side of 1 is configured as a clutch drum 22 of the hydraulic servo 20 of the first clutch C—1
- the hydraulic servo 20 is composed of the planetary gear DP and the hydraulic servo 20 of the second clutch C—1.
- the hydraulic servo 20 of the first clutch C-1 is disposed on the input shaft 12 away from the boss 3b, and hydraulic oil is supplied through the oil passage in the input shaft 12.
- the length of the oil passage can be shortened by not interposing the oil passage in the input shaft 12, thereby improving controllability as the vehicle automatic transmission 1.
- the counter gear 15 is connected to the ring gear R3 of the planetary gear unit PU.
- the counter gear 15 is disposed on the opposite side to the planetary gear DP in the axial direction with respect to the planetary gear unit PU, and the second brake B-2 Is a multi-plate brake composed of a plurality of friction plates 71, and the multi-plate brake is disposed on the outer peripheral side of the planetary gear unit PU.
- the counter gear 15 is connected between the planetary gear unit PU and the planetary gear DP.
- the hub member 117 of the second brake B-2 can be shared with the carrier CR2 in common with the output member 103 on the output side of the second clutch C-2, compared with Compared to the case where a band brake is installed on the outer peripheral side of the transmission member 103 on the output side of the clutch C-2, multiple plates are provided in the outer peripheral side space of the planetary gear unit PU. Allows you to place the brakes, while maintaining a compact I spoon, the brake can be Taiti spoon.
- the counter shaft 81 is arranged in parallel to the input shaft 12 and connected via the counter gear 15 connected to the ring gear R3, and the output rotation from the ring gear R3 1S via the counter gear 15 Since it is transmitted to the countershaft 81, the vehicle automatic transmission 1 can be suitably used for an FF type vehicle.
- the counter gear 15 is disposed on the opposite side to the planetary gear DP with respect to the planetary gear unit PU, and is supported by the support portion 120a connected to the support wall 120 extending from the case 4.
- the distance between the planetary gear DP and the planetary gear unit PU can be shortened, and the output side member 101 of the third clutch C-3 and the output side of the first clutch C-1 that need strength in particular to transmit high torque
- the member 102 can be shortened. This makes it possible to reduce the weight and improve the controllability of the vehicle automatic transmission 1.
- the carrier CR1 is connected to the input shaft 12 on the planetary gear unit PU side with respect to the planetary gear DP, and the second clutch C is connected to the planetary gear DP on the side opposite to the planetary gear unit PU in the axial direction.
- the clutch drum 32 which is the transmission member on the input side of 2
- the transmission member 32 on the input side of the carrier CR1 and the second clutch C 2 and the input shaft 12 can be connected without complicating the members.
- the hub member 116 of the first brake B-1 and the transmission member 104 connected thereto are connected to the sun gear S2 on the side opposite to the planetary gear DP in the planetary gear unit PU,
- the hub member 116 and the transmission member 104 of the brake B-1 and the sun gear S2 can be connected without complicating the members, and the automatic transmission 1 for the vehicle can be connected.
- the planetary gear DP is a carrier that supports the sun gear S1 whose rotation is always fixed with respect to the case 4, the pin-on gear P1, and the pin-on gear P2 rotatably, and is always connected to the input shaft 12. Since it comprises CR1 and a ring gear R1 that meshes with the pinion gear P2 and outputs a reduced speed rotation, it is possible to output a reduced speed rotation that reduces the input rotation of the input shaft 12 from the ring gear R1.
- the planetary gear unit PU includes a sun gear S2, a sun gear S3, a short pinion P3 that meshes with the sun gear S3, and a long pinion P4 that meshes with the sun gear S2 and meshes with the short peer P3, It consists of a radio gear type planetary gear unit PU having a carrier CR2 that rotatably supports the short pinion P3 and the long pinion P4 and a ring gear R3 that meshes with the long pinion P4.
- Rotating element Can be connected to the output side member of each clutch or brake without complication of the members, but high rotation speed of each rotating element can be prevented and a good gear ratio can be obtained. it can.
- the first clutch C-1 is engaged and the second brake B-2 is locked, so that the first forward speed is engaged, and the first clutch C-1 is engaged and the first brake is engaged.
- B-1 the second forward speed is established.
- the first clutch C-1 and the third clutch C-3 the third forward speed is established, and the first clutch C-1 is engaged.
- the fourth clutch C-4 are engaged with the fourth forward speed, and the first clutch C-1 and the second clutch C-2 are engaged with the fifth forward speed.
- the vertical axis indicates the rotation speed of sun gear S2, sun gear S3, carrier CR2, and ring gear R3 of planetary gear unit PU
- the horizontal axis indicates the gears of sun gear S2, sun gear S3, carrier CR2, and ring gear R3.
- the sun gear S2 is positioned at the end of the lateral direction, and is configured correspondingly to the carrier CR2, the ring gear R3 connected to the counter gear 15, and the sun gear S3 in this order. Can do.
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Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007507159A JP4395803B2 (ja) | 2005-03-09 | 2006-03-08 | 車輌用自動変速機 |
CN2006800009298A CN101031738B (zh) | 2005-03-09 | 2006-03-08 | 车辆用自动变速机 |
EP06715417A EP1857709B1 (en) | 2005-03-09 | 2006-03-08 | Automatic transmission for vehicle |
US12/831,729 US8029406B2 (en) | 2005-03-09 | 2010-07-07 | Automatic transmission for a vehicle |
US12/832,264 US7967716B2 (en) | 2005-03-09 | 2010-07-08 | Automatic transmission for a vehicle |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2005-066397 | 2005-03-09 | ||
JP2005066397 | 2005-03-09 |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/831,729 Division US8029406B2 (en) | 2005-03-09 | 2010-07-07 | Automatic transmission for a vehicle |
US12/832,264 Division US7967716B2 (en) | 2005-03-09 | 2010-07-08 | Automatic transmission for a vehicle |
Publications (1)
Publication Number | Publication Date |
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WO2006095784A1 true WO2006095784A1 (ja) | 2006-09-14 |
Family
ID=36953378
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2006/304497 WO2006095784A1 (ja) | 2005-03-09 | 2006-03-08 | 車輌用自動変速機 |
Country Status (6)
Country | Link |
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US (3) | US7819773B2 (ja) |
EP (3) | EP1857709B1 (ja) |
JP (1) | JP4395803B2 (ja) |
KR (1) | KR100870335B1 (ja) |
CN (2) | CN101413567B (ja) |
WO (1) | WO2006095784A1 (ja) |
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JP2009243626A (ja) * | 2008-03-31 | 2009-10-22 | Aisin Aw Co Ltd | 自動変速機 |
DE102007056743B4 (de) * | 2007-08-16 | 2013-02-21 | Hyundai Motor Co. | Automatikgetriebe eines Fahrzeuges |
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CN101413567B (zh) | 2005-03-09 | 2011-05-11 | 爱信艾达株式会社 | 车辆用自动变速机 |
JP5303004B2 (ja) * | 2011-06-07 | 2013-10-02 | ジヤトコ株式会社 | 自動変速機 |
JP6119379B2 (ja) * | 2013-03-29 | 2017-04-26 | アイシン・エィ・ダブリュ株式会社 | 動力伝達装置 |
US9222550B2 (en) * | 2013-06-13 | 2015-12-29 | Ford Global Technologies, Llc | Multi-speed transmission |
US10132404B2 (en) | 2013-06-21 | 2018-11-20 | Ford Global Technologies, Llc | Transmission with integrated clutch and gear set |
DE102016217922A1 (de) | 2016-09-19 | 2018-03-22 | Zf Friedrichshafen Ag | Automatikgetriebe |
JP6495963B2 (ja) * | 2017-03-23 | 2019-04-03 | 本田技研工業株式会社 | 動力伝達装置 |
DE102017121165A1 (de) | 2017-09-13 | 2017-11-02 | FEV Europe GmbH | Getriebesystem mit großer Gangzahl |
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Also Published As
Publication number | Publication date |
---|---|
EP1857709A4 (en) | 2010-07-07 |
EP2333375A2 (en) | 2011-06-15 |
US7967716B2 (en) | 2011-06-28 |
CN101413567A (zh) | 2009-04-22 |
EP2333375B1 (en) | 2013-03-06 |
US20100298087A1 (en) | 2010-11-25 |
CN101031738B (zh) | 2010-06-09 |
JP4395803B2 (ja) | 2010-01-13 |
EP1857709B1 (en) | 2012-04-25 |
EP2339210A3 (en) | 2011-12-28 |
US8029406B2 (en) | 2011-10-04 |
EP1857709A1 (en) | 2007-11-21 |
US20080125280A1 (en) | 2008-05-29 |
JPWO2006095784A1 (ja) | 2008-08-14 |
KR20070057213A (ko) | 2007-06-04 |
CN101413567B (zh) | 2011-05-11 |
EP2339210B1 (en) | 2013-11-06 |
EP2333375A3 (en) | 2011-12-28 |
KR100870335B1 (ko) | 2008-11-25 |
CN101031738A (zh) | 2007-09-05 |
EP2339210A2 (en) | 2011-06-29 |
US7819773B2 (en) | 2010-10-26 |
US20100298085A1 (en) | 2010-11-25 |
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