WO2007114215A1 - 自動変速機 - Google Patents
自動変速機 Download PDFInfo
- Publication number
- WO2007114215A1 WO2007114215A1 PCT/JP2007/056794 JP2007056794W WO2007114215A1 WO 2007114215 A1 WO2007114215 A1 WO 2007114215A1 JP 2007056794 W JP2007056794 W JP 2007056794W WO 2007114215 A1 WO2007114215 A1 WO 2007114215A1
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- WO
- WIPO (PCT)
- Prior art keywords
- gear
- clutch
- planetary gear
- compound planetary
- brake
- Prior art date
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 67
- 150000001875 compounds Chemical class 0.000 claims description 123
- 230000002093 peripheral effect Effects 0.000 claims description 37
- 238000010586 diagram Methods 0.000 claims description 27
- 241000920340 Pion Species 0.000 claims description 24
- 239000002184 metal Substances 0.000 description 8
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 238000007599 discharging Methods 0.000 description 7
- 238000003466 welding Methods 0.000 description 6
- 239000012530 fluid Substances 0.000 description 5
- 241000135194 Pione Species 0.000 description 4
- 230000009977 dual effect Effects 0.000 description 4
- 239000000969 carrier Substances 0.000 description 3
- 238000001514 detection method Methods 0.000 description 3
- 239000000463 material Substances 0.000 description 2
- 230000013011 mating Effects 0.000 description 2
- 235000014443 Pyrus communis Nutrition 0.000 description 1
- KYKAJFCTULSVSH-UHFFFAOYSA-N chloro(fluoro)methane Chemical compound F[C]Cl KYKAJFCTULSVSH-UHFFFAOYSA-N 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
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
- 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
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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
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three 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
- F16H2200/2048—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
Definitions
- the present invention makes it possible to connect each element of the first and second compound planetary gears to the input shaft via a clutch and to fix the input shaft by a plurality of stages by fixing the elements via a brake.
- the present invention relates to an automatic transmission that shifts gears to an output shaft.
- an input shaft, a first compound planetary gear, a second compound planetary gear, and an output shaft are arranged on a common axis in a transmission case, and each element of the first and second compound planetary gears is a clutch.
- the first compound planetary gear 60 includes a common sun gear S1S2 connected to the input shaft 15, a long pinion 63 and a long pin that mesh with the common sun gear S1S2.
- a common carrier C1C2 that can be fixed via the second brake B-2 and the long pinion 63 while supporting the pinion 64 that mates with the on 63 and the first brake B-1
- the first ring gear R1 that can be fixed and the second ring gear R2 that can mesh with the pione 64 and can be fixed via the third brake B-3.
- the second compound planetary gear 17 includes third and fourth sun gears S3 and S4 that are directly connected to the input shaft 15 via the first clutch C-1, and third and fourth sun gears S3 and S4 and a pinion 33.
- Patent Document 1 Japanese Patent Laid-Open No. 2002-213545 (Page 8, Fig. 4)
- the present invention provides a compact, first compound planetary gear by disposing the first to third clutches that selectively connect the input shaft to the first and second compound planetary gears in front of the first compound planetary gear.
- the objective is to provide a forward 8-speed automatic transmission that can keep the relative rotation of the sun gear and ring gear small.
- the structural feature of the invention according to claim 1 is that the input shaft, the output shaft, and four pieces arranged sequentially at intervals corresponding to the gear ratio in the velocity diagram.
- the first compound planetary gear having the first, second, third, and fourth elements corresponding to the elements in the order of arrangement, and four elements arranged in order at intervals corresponding to the gear ratio in the speed diagram.
- a second compound planetary gear having fifth, sixth, seventh, and eighth elements respectively corresponding to each other, and the first element is connectable to the input shaft via a third clutch.
- a second sun gear which is rotatably supported on a common carrier and meshes with each other via a long pinion and a pin which mesh with each other, and the second element is directly connected to the fifth element.
- One of the long pion and the pion and The third element is the common carrier that can be fixed via a first brake, and the fourth element can be fixed via a third brake.
- the sixth element can be connected to the input shaft via a second clutch and can be fixed via a fourth brake, and the seventh element can be fixed to the input shaft via a second brake.
- the eighth element can be connected to the input shaft via a first clutch, and the first to third clutches, the first compound planetary gear, and the second compound planetary gear are The first to third clutches, the first compound planetary gear, and the second compound planetary gear are arranged in this order in the axial direction, and the third brake and the first sun gear are arranged on the first to third clutch side. is there.
- the constitutional feature of the invention according to claim 2 corresponds to the input shaft, the output shaft, and the four elements sequentially arranged at intervals corresponding to the gear ratio in the speed diagram, respectively.
- the first compound planetary gear having the first, second, third, and fourth elements, and the four elements sequentially arranged at intervals corresponding to the gear ratio in the velocity diagram, respectively correspond to the arrangement order.
- a second compound planetary gear having sixth, seventh and eighth elements.
- the first element is connectable to the input shaft via a third clutch and is rotatably supported by a common carrier.
- the fourth carrier is a first ring gear that can be fixed via a third brake and meshed with the long pion, and can be fixed via a first brake.
- the fifth element can be fixed via a second brake
- the sixth element can be connected to the input shaft via a second clutch, and can be fixed via a fourth brake.
- the 8th element is connectable to the input shaft via a first clutch, the first to third clutches, the first compound planetary gear,
- the second compound planetary gear is arranged in the order of first to third clutches, first compound planetary gear, and second compound planetary gear in the axial direction, and the first brake is arranged on the first to third clutch side. It is when.
- the structural feature of the invention of claim 3 is that in claim 1 or 2, the clutch drum of the second clutch and the third clutch is a shared clutch drum.
- a structural feature of the invention according to claim 4 is that, in claim 3, the first clutch is disposed inside the second and third clutches.
- the structural feature of the invention according to claim 5 is that, according to claim 3 or 4, the hydraulic servo section of the second and third clutches is connected to the common clutch drum at the bottom wall of the common clutch drum. They are provided on the rear side and the front side, respectively.
- the structural feature of the invention of claim 6 is that, in claim 5, the servo chamber of the hydraulic servo section of the second clutch is located on the rear surface side of the bottom wall of the common clutch drum.
- a piston that is slidably fitted to a rear portion of the base end portion of the drum and an inner peripheral surface of the bent portion of the bottom wall, and the servo chamber of the hydraulic servo portion of the third clutch includes On the front side of the bottom wall, an oil passage that is defined by a piston that is slidably fitted to the front portion of the base end portion and the outer peripheral surface of the bent portion, and that opens to each servo chamber is described above. It is provided at the base end.
- the structural feature of the invention of claim 7 is that, in claim 6, a base end portion of the common clutch drum protrudes behind a front wall member fixed to a front end surface of the transmission case.
- the oil passage force that is rotatably supported by the boss portion and opens to each servo chamber is communicated with each oil passage provided in the boss portion via a distributor.
- the structural feature of the invention according to claim 8 is that, in any one of claims 1 to 7, in the second compound planetary gear, the fifth element is a third ring gear, The sixth element is a third carrier that supports the third pinion and a fourth ring gear R4 directly connected to the third carrier, and the seventh element is a fourth carrier that supports the fourth pinion, The eighth element is a third sun gear meshed with the third ring gear via the third pinion, and a fourth sun gear meshed directly with the third sun gear and meshed with the fourth ring gear via the fourth pinion. It is to be.
- the first element of the first compound planetary gear can be connected to the input shaft via the third clutch.
- the 4th element of the 1st compound planetary gear reversely rotates and the 1st element It is possible to prevent a large relative rotation from occurring.
- first to third clutches that allow the input shaft to be connected to the first element of the first compound planetary gear and the second and fourth elements of the second compound planetary gear are combined in front of the first compound planetary gear. Because of this arrangement, the forward 8-speed automatic transmission can be made extremely compact, reducing weight and cost.
- the first compound planetary gear is a second sun gear as a first element, a long pion that is rotatably supported by a common carrier and meshes with each other, and a second pear that meshes with the second sun gear. It consists of a common ring gear as an element, a common carrier as a third element, and a first ring as a fourth element that mates with a common ring gear via a long pion or pion. It is possible to provide a compact forward 8-speed automatic transmission.
- the first to third clutches, the first compound planetary gear, and the second compound planetary gear arranged together in the front are arranged in this order in the axial direction, and the third brake and the first sun gear are Since it is arranged on the 1st to 3rd clutch side, the 3rd brake that can fix the 1st sun gear, which is the 4th element of the 1st compound planetary gear, is connected between the 1st to 3rd clutch and the 1st compound planetary gear. It can be placed in a compact.
- the first element of the first compound planetary gear can be connected to the input shaft via the third clutch.
- the third clutch By cutting the latch, it is possible to prevent the fourth element of the first compound planetary gear from rotating backward and causing a large relative rotation with the first element.
- first to third clutches that allow the input shaft to be connected to the first element of the first compound planetary gear and the second and fourth elements of the second compound planetary gear are combined in front of the first compound planetary gear. Because of this arrangement, the forward 8-speed automatic transmission can be made extremely compact, reducing weight and cost.
- the first compound planetary gear includes a common sun gear as a first element, a second ring gear as a second element that meshes with a long pion rotatably supported by a common carrier, and a second ring gear. It consists of a common carrier as three elements and a first ring gear as a fourth element that mates with a common sun gear via a long pion. It can provide an 8-speed automatic transmission.
- the first to third clutches, the first compound planetary gear, and the second compound planetary gear that are arranged together in the front are arranged in this order in the axial direction, and the first brake includes the first to third clutches. Because it is arranged on the clutch side, the first brake that can fix the common carrier, which is the third element of the first compound planetary gear, is compactly arranged between the first to third clutches and the first compound planetary gear. can do.
- the first clutch is disposed inside the second and third clutches, the first to third clutches are disposed in a small space. It is possible to reduce the size, weight, and cost of an 8-speed automatic transmission.
- the hydraulic servo unit force common clutch drum of the second and third clutches are provided on the rear surface side and the front surface side of the bottom wall, respectively.
- the hydraulic servos of the second and third clutches can be placed in a small space
- the servo chambers of the hydraulic servo portions of the second and third clutches are provided on the rear side and the front side of the bottom wall of the common clutch drum!
- Each servo chamber is defined by a rear portion and a front portion of the base end portion of the common clutch drum, and pistons slidably fitted to the inner peripheral surface and the outer peripheral surface of the bent portion of the bottom wall, respectively.
- An oil passage opening at the base is provided at the base end.
- the base end portion of the common clutch drum is rotatably supported by the boss portion of the front wall member fixed to the transmission case, and the second, The oil passages that open to the servo chamber of the third clutch communicate with each oil passage provided in the boss portion via a distributor.
- the configuration of the second and third clutches can be simplified, and an oil passage for supplying and discharging hydraulic pressure can be easily provided in each servo chamber.
- the second compound planetary gear is configured to rotatably support the third and fourth sun gears directly connected to each other and the third and fourth pinions, respectively.
- the third and fourth carriers the third ring gear that meshes with the third sun gear via the third pion, the meshed via the fourth sun gear and the fourth pion, and the first sun gear that is directly connected to the third sun gear. It consists of 4 ring gears.
- an automatic transmission having a simple configuration having a gear ratio of 8 forward speeds and at least 1 reverse speed.
- FIG. 1 is a skeleton diagram showing a first embodiment of an automatic transmission according to the present invention.
- FIG. 2 is a diagram showing an operation table of brakes and clutches at each shift speed according to the first embodiment.
- FIG. 3 is a speed diagram showing a rotation ratio of each element of the planetary gear at each gear position in the first embodiment.
- FIG. 4 is a block diagram showing a control device.
- FIG. 5 is a sectional view showing a specific overall configuration of the automatic transmission.
- FIG. 6 is an enlarged cross-sectional view showing the first to third clutch portions of FIG.
- FIG. 7 is an enlarged cross-sectional view showing the first and second compound planetary gear portions of FIG.
- FIG. 8 is a skeleton diagram showing a second embodiment.
- FIG. 9 is a speed diagram showing a rotation ratio of each element of the planetary gear at each shift speed according to the second embodiment.
- FIG. 10 is a skeleton diagram showing a third embodiment.
- FIG. 11 is a velocity diagram showing a rotation ratio of each element of the planetary gear at each shift speed in the third embodiment.
- reference numeral 10 denotes an automatic transmission according to the present invention, which is used, for example, to shift the output rotation of a fluid torque converter 11 that is driven to rotate by an automobile engine and transmit it to drive wheels.
- the automatic transmission 10 includes an input shaft 14, a first compound planetary gear 15, a second compound planetary gear 16, an output shaft 17, first, first, 2, 3rd clutch Cl, C-2, C_3 and 1st, 2nd, 3rd, 4th brake ⁇ -1, ⁇ -2, B-3, B-4, one-way clutch Fl, etc. ing.
- the first compound planetary gear 15 is capable of rotating the first and second sun gears SI and S2 rotatably supported on the common axis 13 and the long pinion 18 and the pinion 19 that mesh with each other. It consists of a common carrier C1C2 to be supported and a common ring gear R1R2 that meshes with the first sun gear S1 via the long pinion 18 and meshes with the second sun gear S2 via the long pinion 18 and pinion 19. Yes.
- the second compound planetary gear 16 is a common carrier that supports the third and fourth sun gears S3 and S4 and the third and fourth pinions 20 and 21 that are rotatably supported and directly connected to the common axis 13. C3C4, and third and fourth sun gears S3 and S4 and third and fourth ring gears R3 and R4 that are respectively coupled via third and fourth pinions 20 and 21. Direct connection is directly connected without a clutch.
- the first sun gear S1 can be fixed via the third brake B-3, and the second sun gear S2 is connected to the input shaft 14 via the third clutch C-3.
- the common carrier C1C2 can be fixed via the first brake B-1, and the common ring gear R1 R2 is directly connected to the third ring gear R3 of the second compound planetary gear 16.
- the second compound planetary gear 16 is configured such that the directly connected third and fourth sun gears S3 and S4 can be connected to the input shaft 14 via the first clutch C-1, and the directly connected third carrier C3.
- the fourth ring gear R4 can be connected to the input shaft 14 via the second clutch C-2 and can be fixed via the fourth brake B-4, and in parallel with the fourth brake B-4. It is connected to the case 12 via the arranged one-wake latch F-1 to prevent reverse rotation, the third ring gear R3 can be fixed via the second brake B-2, and the fourth carrier C-4 is , Directly connected to output shaft 17.
- the pump impeller 22 of the fluid torque converter 11 is driven to rotate by an unillustrated engine to send out oil, and the stator 23 receives the reaction force of the oil and generates torque in the turbine 24. .
- the input shaft 14 is directly connected to the turbine 24.
- Reference numeral 25 denotes a lock-up clutch that allows the pump impeller 22 and the turbine 24 to be connected.
- the automatic transmission 10 configured as described above selectively engages the first to third clutches Cl to C-3 and selects the first to fourth brakes ⁇ -1 to ⁇ -4. Are engaged, and the input shaft 14, the output shaft 17, the first compound planetary gear 15 and the second compound planetary gear 16 are selectively connected or fixed to each other, thereby shifting the forward 8th speed and the reverse 2nd speed. Can be established.
- white circles are added to the columns corresponding to the first to third clutches Cl to C-3, the first to fourth brakes B-1 to ⁇ -4, and the one-way clutch F-1. If it is, the clutch is engaged and connected, and the brake is engaged and fixed. When the black circles are attached, the force is supplied to the hydraulic servo in preparation for shifting so that the shifting can be performed smoothly. Torque is transmitted in the clutch, and the reaction force is supported in the brake.
- the number of teeth of the first to fourth sun gears SI, S2, S3, S4 is Zsl, Zs2, Zs3, Zs4, the common ring gear R1R2 and the number of teeth of the third and fourth ring gears R3, R4 are Zrl2, Zr3, Zr4.
- Nr (1 + ⁇ ) Nc- I Ns- ⁇ -(1)
- Nr (1—E) Nc + Ns' ⁇ ⁇ (2)
- the first and second compound planetary gears 15 , 16 speed ratios are as shown in the speed diagram in Fig. 3.
- the speed diagram shows the planetary gear sun gear, carrier and ring gear force elements arranged at intervals corresponding to the gear ratio in the horizontal axis direction and the speed ratio corresponding to each element in the vertical axis direction. It is.
- FIG. 3 shows the velocity diagrams of the first and second compound planetary gears 15 and 16 side by side.
- first compound planetary gear 15 In the first compound planetary gear 15, the first carrier C1 and the second carrier C2, and the first ring gear R1 and the second ring gear R2 of the single pinion planetary gear 26 and the double beon planetary gear 27 are shared. And the speed ratio of common carrier C1C2 and common ring gear R1R2 is shown on each vertical line with Rl and R2 attached.
- the third and fourth sun gears S3 and S4 of the single-pione planetary gear 26 are directly connected, and the third carrier C3 and the fourth ring gear R4 are directly connected, so that SI, S2 and C3,
- the speed ratio of the third and fourth sun gears S3 and S4, the third carrier C3 and the fourth ring gear R4 is shown on each vertical line with R4 attached thereto.
- the interval between the vertical line of the common carrier C1C2 and the vertical line of the first sun gear S1 is regarded as 1, and the vertical line of the common ring gear R1R2 is the same as that of the common carrier C1C2.
- Vertical line force Sun gear S1 is arranged on the opposite side of the vertical line by a distance of ⁇ 1.
- the distance between the vertical line of common carrier C1C2 and the vertical line of second sun gear S2 is regarded as 1
- the vertical line of common ring gear R1 R2 is the vertical line force of common carrier C1C2. Is arranged on the same side as the vertical line with a gear ratio ⁇ 2.
- Second compound planetary gear 16 single-pione planetary For the tally gear 26, the distance between the vertical lines of the third and fourth carriers C3 and C4 and the vertical lines of the third and fourth sun gears S3 and S4 is regarded as 1, and the vertical lines of the third and fourth ring gears R3 and R4 are regarded as 1.
- the lines are arranged at a distance of 3, ⁇ 4 on the opposite side of the vertical lines of the third and fourth sun gears S3 and S4, respectively, on the vertical lines of the third and fourth carriers C3 and C4.
- the speed diagram shows that the first to third clutches C-l to C-3, the first to fourth brakes ⁇ -1 to ⁇ -4, and the one-way clutch F-1 were selectively operated. -1 to C-3, Bl to B-4, and Fl are entered.
- the elements corresponding to the four vertical lines are the first, second, third, and fourth in the order of the right force of the vertical lines.
- the elements corresponding to the four vertical lines are the fifth, sixth, seventh, and eighth elements in order from the left of the vertical line.
- the second sun gear S2 of the first compound planetary gear 15 is the first element
- the common ring gear R1R2 is the second element
- the common carrier C1C2 is the third element
- the first sun gear S1 is the fourth element.
- the third ring gear R3 of the second compound planetary gear 15 is the fifth element
- the third carrier C3 and the fourth ring gear R4 are the sixth element
- the fourth carrier C4 is the seventh element
- the third and fourth sun gears S3 and S4 are 8th element.
- the control device 30 with a built-in CPU includes an engine speed sensor 31 that detects the engine speed Ne of the torque converter 11 to which the engine speed is transmitted, and an input speed sensor 32 that detects the speed Ni of the input shaft 14. , Output speed sensor 33 that detects the speed Nv of the output shaft 17, Range position for sending detection signals D, N, R when the shift lever is shifted to drive range D, neutral range N, reverse range R Sensor 34, throttle opening sensor 35 that detects accelerator depression amount Ss equal force Each detection signal is input, the most suitable gear is selected based on these detection signals, and the control current is applied to each clutch and brake.
- the first speed (1st) is achieved by the engagement of the first clutch C-1 and the automatic engagement of the one-way clutch F-1 by the control device 30.
- the rotation of the input shaft 14 is input to the third and fourth sun gears S3 and S4 of the second compound planetary gear 16 via the first clutch C-1, and the third carrier C3 and the fourth Since the ring gear R4 is prevented from reverse rotation by the one-way clutch Fl and receives a reaction force, the fourth carrier C4 and the output shaft 17 are decelerated at the gear ratio of the first speed and rotated forward.
- the second speed (2nd) is achieved by engagement of the first clutch C-1 and the second brake B-2.
- the rotation of the input shaft 14 is input to the third and fourth sun gears S3 and S4 of the second compound planetary gear 16 via the first clutch C-1, and the third ring gear R3 is fixed by the second brake B-2. Therefore, the fourth carrier C4 and the output shaft 17 are decelerated at the gear ratio of the second speed and rotated forward.
- the third speed (3rd) is achieved by engagement of the first and third clutches C_l, C_3 and the first brake B_l.
- the rotation of the input shaft 14 is input to the second sun gear S2 of the first compound planetary gear 15 via the third clutch C-3, and the common carrier C1C2 is fixed via the first brake B-1 to Rotational force of common ring gear R1R2 with reduced rotation of 14 Transmitted to third ring gear R3 of dual planetary gear 16 directly connected to common ring gear R1R2, and rotation of input shaft 14 is transmitted to third and fourth sun gears S3, S3 of dual planetary gear 16 Since the signal is input to S4 via the first clutch C-1, the output of the fourth carrier C4 and the output shaft 17 is decelerated at the gear ratio of the third speed and is rotated forward.
- the fourth speed (4th) is achieved by engagement of the first, third clutches C-1, C-3 and the third brake B-3.
- the rotation of the input shaft 14 is input to the second sun gear S2 of the first compound planetary gear 15 via the third clutch C-3, and the first sun gear S1 is fixed via the third brake B-3.
- Rotational force of common ring gear R1R2 with reduced rotation of input shaft 14 Rotation of input planetary gear 16 is transmitted to third ring gear R3 of dual planetary gear 16 directly connected to common ring gear R1R2, and third and fourth sun gears of dual planetary gear 16 Since the signal is input to S3 and S4 via the first clutch C-1, the fourth carrier C4 and the output shaft 17 are decelerated at the gear ratio of the fourth speed and are rotated forward.
- the fifth speed (5th) is achieved by engagement of the first and second clutches Cl and C-2. 3rd carrier C3 and 4 directly connected to the third and fourth sun gears S3 and S4 directly connected to the second compound planetary gear 16 through the first and second clutches Cl and C-2.
- the second compound planetary gear 16 is rotated by one body, and the fourth carrier C4 and the output shaft 17 are rotated forward at the same speed as the input shaft 14 at the fifth gear ratio.
- the sixth speed (6th) is achieved by engagement of the second and third clutches C-2, C-3 and the third brake B-3.
- the rotation of the input shaft 14 is input to the second sun gear S2 of the first compound planetary gear 15 via the third clutch C-3, and the first sun gear S1 is fixed via the third brake B-3.
- the seventh speed (7th) is achieved by engagement of the second and third clutches C-2, C-3 and the first brake B-1.
- the rotation of the input shaft 14 is input to the second sun gear S2 of the first compound planetary gear 15 via the third clutch C-3, and the shared carrier C1C2 is fixed via the first brake B-1 to Rotational force of common ring gear R1R2 with reduced rotation of shaft 14
- Common ring gear Transmitted to third ring gear R3 of second planetary gear 16 directly connected to R1R2 and directly connected third carrier C3 and fourth ring gear R4 are second Since it is connected to the input shaft 14 via the clutch C-2, the fourth carrier C4 and the output shaft 17 are increased in speed by the gear ratio of the seventh speed and rotated forward.
- the eighth speed (8th) is achieved by engagement of the second clutch C-2 and the second brake B-2.
- the rotation of the input shaft 14 is input to the third carrier C3 and the fourth ring gear R4 directly connected to the second compound planetary gear 16 through the second clutch C-2, and the third ring gear R3 is input to the second brake B-2. Accordingly, the fourth carrier C4 and the output shaft 17 are increased in speed by the gear ratio of the eighth speed and rotated forward.
- the first reverse speed (Revl) is achieved by engagement of the third clutch C-3 and the first and fourth brakes B-1, B-4.
- the rotation of the input shaft 14 is shifted to the second sun gear S2 of the first compound planetary gear 15.
- 3Input via clutch C-3, and shared carrier C1C2 is fixed via first brake B-1.By this, the rotational force of common ring gear R1R2 that reduces the rotation of input shaft 14 is directly connected to common ring gear R1R2.
- the third carrier C3 and the fourth ring gear R4 which are transmitted to the third ring gear R3 of the second planetary gear 16 and directly connected to each other, are fixed via the fourth brake B-4.
- the output shaft 17 is decelerated at the gear ratio of reverse 1st speed and rotated in reverse.
- the second reverse speed (Rev2) is achieved by engagement of the third clutch C-3 and the third and fourth brakes B-1 and B-4.
- the rotation of the input shaft 14 is input to the second sun gear S2 of the first compound planetary gear 15 via the third clutch C-3, and the shared carrier C1C2 is fixed via the third brake B-1, so that the input shaft Rotational force of common ring gear R1R2 with reduced rotation of 14 Common ring gear R1R2 is connected directly to the third ring gear R3 of the second compound planetary gear 16
- the third carrier C3 and the fourth ring gear R4 are directly connected to the fourth ring gear R4. Since it is fixed via the brake B-4, the fourth carrier C4 and then the output shaft 17 are decelerated at the gear ratio of reverse 2nd speed and rotated in reverse.
- Gear ratios of the first and second compound planetary gears 15, 16 of the single-pione planetary gear 26 and the double-pione planetary gear 27 ⁇ ⁇ , ⁇ 2, ⁇ 3, ⁇ 4 (the number of teeth of the sun gear ⁇ of the ring gear (Number of teeth) is set to, for example, 0.520, 0.440, 0.394, 0.394, and the gear ratio at each gear stage is calculated based on equations (1) and (2).
- the gear ratio between the input shaft 14 and the output shaft 17 at the gear stage is 3.538 for the first speed, 2.060 for the second speed, 1.405 for the third speed, 1.185 for the fourth speed, 5th speed 1.000, 6th speed 0.821, 7th speed 0.813, 8th speed 0.882, reverse 1st speed 3.168, reverse 2nd speed 2.001 Appropriate value.
- the step between each gear ratio is 1.717 between 1st and 2nd speed, 1.467 between 2nd and 3rd speed, 1.186 between 3rd and 4th speed, between 1186, 4th and 5th speed 1.
- the transmission case 12 includes a bottomed cylindrical transmission case body 12a and its transmission body.
- the rear case 12b is fixed to the bottom with a bolt 44, and a front wall member 43 is fixed to the front end surface of the transmission case main body 12a with a bolt 44.
- An oil pump body 46 that accommodates the oil pump 45 is fixed to the front end surface of the front wall member 43 by bolts 47, and the rear side of the oil pump 45 is blocked by the front wall member 43 !.
- the front wall member 43 has a boss portion 43a extending rearward of the inner peripheral portion force thereof.
- the stator shaft 50 is press-fitted and fixed to the inner peripheral surface of the boss portion 43a, and the input shaft 14 is connected to the stator shaft 50. It is supported by a dollar bearing 51 and a metal bearing 52 so as to be rotatable around a common axis 13.
- a bearing hole 53 is provided at the rear end portion of the input shaft 14, and the end of the intermediate shaft 54 is supported by the shaft bearing hole 55 so as to be coaxially and relatively rotatable.
- the rear end of the intermediate shaft 54 is rotatably supported by a metal bearing 57 in a support hole 56 provided at the front end of the output shaft 17.
- the output shaft 17 is rotatably supported by a dollar bearing 58, a ball bearing 59, and a thrust bearing 60 on the bottom wall 12b and the rear case 12b of the transmission case body 12a.
- the oil pump body 46 is rotatably supported by a hollow rotor 61 cartridge bearing 62 which is connected to an engine output shaft (not shown) and has a pump impeller 22 of a fluid torque comparator 11 provided inside.
- a turbine 32 facing the pump impeller 22 is fitted to the tip of the input shaft 14 while restricting relative rotation.
- a lockup clutch 25 that mechanically couples them via a spring damper 63.
- a stator 23 is supported on the stator shaft 50 via a one-way clutch 64.
- the fluid torque converter 11 side is referred to as the front
- the output shaft 17 side is referred to as the rear.
- First to third clutches C-1, C-2, and C-3 are collectively disposed in front of the first compound planetary gear 15 at a front portion of the transmission case 12.
- the base end portion 65a of the common clutch drum 65 shared by the second and third clutches C-2 and C_3 can be rotated by the one-dollar bearing 66 and the thrust bearing 67 in the box portion 43a of the front wall member 43. It is supported.
- the common clutch drum 65 is spline-fitted to the outer peripheral surface of the input shaft 14 at the inner peripheral surface of the base end cylindrical portion protruding rearward from the base end portion 65a, and is rotationally connected to the input shaft 14.
- Shared clutch drum 65 the bottom wall 65b projects radially from the base end 65a, and the cylindrical portion 65c extends rearward from the outer periphery of the bottom wall 65b.
- the second and third hub members 68, 69 are sequentially arranged on the inner periphery of the cylindrical portion 65c, and the forward force is sequentially arranged.
- the cylindrical portion 65c inner peripheral surface of the common clutch drum 65 and the cylinders of the second and third hub members 68, 69 are provided.
- a plurality of separator plates 72 and 73 and a plurality of friction plates 74 and 75 constituting the friction engagement portions 70 and 71 of the second and third clutches C-2 and C-3 are alternately arranged on the outer peripheral surfaces of the portions 68a and 69a.
- the spline is engaged.
- the second hub member 68 is bent rearward in the radial direction, and is fixed to a flange portion formed at the front end of the cylindrical connecting shaft 77 supported by the metal shaft 76 on the intermediate shaft 54 by welding or the like.
- the connecting shaft 77 is spline-fitted with the third carrier C3 of the second compound planetary gear 16 at the rear end.
- the third hub member 69 is bent rearward in the radial direction, and fixed to the radially extending portion of the connecting member 79 by welding or the like.
- the connecting member 79 is a cylindrical portion extending rearward thereof.
- the connecting member 79 is supported by a metal bearing 78 on the inner peripheral surface of the cylindrical portion extending forward of the first sun gear S1 of the first compound planetary gear 15.
- the outer peripheral surface of the cylindrical portion extending forward is fitted with a spline.
- the first clutch C-1 is disposed inside the second and third clutches C-2, C-3.
- the first clutch drum 80 of the first clutch C-1 is disposed on the inner periphery of the second knob member 68, and the first clutch drum 80 is bent and input in the radial direction after the cylindrical portion 80a extends forward. It is fixed to the shaft 14 by welding.
- a first hub member 81 is disposed on the inner periphery of the cylindrical portion 80a.
- the friction engagement portion 82 of the first clutch C_l is provided on the inner peripheral surface of the cylindrical portion 80a and the outer peripheral surface of the cylindrical portion 81a of the first hub member 81.
- a plurality of separator plates 83 and a plurality of friction plates 84 constituting the same are alternately splined.
- the first hub member 81 is bent rearward in the radial direction and is splined to the intermediate shaft 54.
- a thrust bearing 85 is interposed between the front end surface of the first hub member 81 and the rear end surface of
- the hydraulic servo portion 86 of the second clutch C-2 is a cylinder 87 formed by a base end cylindrical portion projecting rearward of the base end portion 65a of the common clutch drum 65 and a bent portion inner peripheral surface of the bottom wall 65b.
- the piston 88 is slidably fitted to the cylinder 87, and the servo chamber 89 force S between the cylinder 87 and the piston 88 is defined in an oil-tight manner.
- a cancel plate 90 is fitted to the base end cylindrical portion protruding rearward of the base end portion 65a by restricting rearward movement by a snap ring. Separator plate 72 and friction plate 74 are not connected between cancel plate 90 and the rear surface of piston 88.
- a compression spring 91 biasing in the connecting direction is interposed, and a cancel chamber 92 for canceling the centrifugal hydraulic pressure generated in the servo chamber 89 is provided.
- An abutting portion that protrudes rearward and outward from the piston 88 is opposed to the foremost separator plate 72 of the second clutch C-2.
- An oil passage 109 that opens into the servo chamber 89 is formed in the base end portion 65a of the common clutch drum 65, and the oil passage 109 is formed in the boss portion 43a of the front wall member 43 in the axial direction.
- the oil passage 110 is communicated via a distributor 111 interposed between the outer peripheral surface of the boss portion 43a and the outer peripheral surface of the base end portion 65a, and the oil passage 110 is connected via a hydraulic servo valve (not shown).
- the oil passage 112 is communicated with the discharge port of the oil pump 45 through the oil passage 112 formed in the boss portion 43a.
- the hydraulic servo section 93 of the third clutch C-3 is slidably fitted to the outer peripheral surface of the front end portion 65a of the common clutch drum 65 and the outer peripheral surface of the bent portion of the bottom wall 65b.
- the servo chamber 96 is defined in an oil-tight manner by the outer peripheral surface of the base end portion 65a, the outer peripheral surface of the bent portion of the bottom wall 65b, and the piston 95.
- a cancel plate 97 is fitted to the front end portion of the base end portion 65a such that the forward movement is restricted by snap ringing.
- a compression spring 98 is interposed between the cancel plate 97 and the piston 95 to urge the separator plate 73 and the friction plate 75 in the non-connecting direction, and cancels the centrifugal hydraulic pressure generated in the servo chamber 96 Cancel Room 99 is provided.
- Piston 95 is fixed to the outer periphery of the rear end of the piston 95 by welding etc.
- the contact member 108 faces the separator plate 73 at the rearmost end of the third clutch C-3.
- An oil passage 113 that opens into the servo chamber 96 is formed in the base end portion 65a of the common clutch drum 65, and the oil passage 113 is formed in the boss portion 43a of the front wall member 43 in the axial direction.
- the oil passage 114 communicated with the distributor 111 through the distributor 111, and the oil passage 114 communicated with the discharge port of the oil pump 45 through the oil passage 112 through a hydraulic servo valve (not shown).
- the hydraulic servo portions 86 and 93 of the second and third clutches C-2 and C-3 are provided on the common clutch drum 65 on the front side and the rear side of the bottom wall 65b, respectively.
- the hydraulic servo sections 86 and 93 of the second and third clutches C-2 and C-3 can be arranged in a small space. That is, the servo chamber 89 of the hydraulic servo section 86 of the second clutch C-2 is formed on the rear surface side of the bottom wall 65b of the common clutch drum 65, the rear portion of the base end 65a of the common clutch drum 65, and the clutch drum.
- the servo chamber 96 of the hydraulic servo section 93 of the third clutch C-3 is defined by the piston 88 that is slidably fitted to the inner peripheral surface of the bent portion of the bottom wall 65b of the 65.
- a piston 95 is slidably fitted to the front part of the base end part 65a of the common clutch drum 65 and the outer peripheral surface of the bent part of the bottom wall 65b of the clutch drum 65.
- the oil passage 109, 113 force that is defined and opens in the servo chambers 89, 96 is provided in the S base end 65a.
- the hydraulic servo sections 86 and 93 of the second and third clutches C-2 and C-3 can be made simple and compact, and the oil passages for supplying and discharging hydraulic pressure to the servo chambers 89 and 96 are provided. Can be easily provided.
- the oil passage 110, 11 4 force S chlorofluorocarbon wall material 43 boss The oil passage 109, 113 and the oil passage 110, 114 are connected with the force ⁇ distributor 111, so the hydraulic chambers 89, 96 of the second and third clutches C-2, C-3 are hydraulically connected.
- An oil passage for supplying and discharging can be easily provided.
- the hydraulic servo unit 100 of the first clutch C-1 is slidably fitted with a piston 102 to a cylinder 101 formed by the bottom of the first clutch drum 80 and the outer peripheral surface of the input shaft 14.
- a servo chamber 103 is formed in an oil-tight manner between the Linda 101 and the piston 102.
- a cancel plate 104 is fitted to the rear end portion of the input shaft 14 with its axial movement restricted by a snap ring.
- a compression spring 105 that urges the separator plate 83 and the friction plate 84 in a non-connecting direction is interposed between the cancel plate 104 and the piston 102, and the centrifugal hydraulic pressure generated in the servo chamber 103 is canceled.
- a cancellation chamber 106 is provided.
- An oil passage 115 that opens to the servo chamber 103 is formed in the rear end portion of the input shaft 14, and the oil passage 115 is formed in the boss portion 43a of the front wall member 43 in the axial direction.
- the oil passage 116 is communicated via a distributor 117 formed between the outer peripheral surface of the input shaft 14 and the inner peripheral surface of the boss portion 43a, and the oil passage 116 is connected to the oil passage via a hydraulic servo valve (not shown). It is connected to the discharge port of oil pump 45 through 112.
- the first compound planetary gear 15 is disposed on the common axis line 13 behind the first clutch C-1, and the second sun gear S2 is rotatably supported by a metal bearing on the outer periphery of the connecting shaft 77, and at the front end.
- the connecting member 79 is spline-engaged with the inner peripheral surface of the cylindrical portion.
- the first sun gear S1 is rotatably supported by a metal bearing across the cylindrical portion extending in front of the second sun gear S2 and the cylindrical portion of the connecting member 79.
- a common carrier C1C2 is rotatably supported by a metal bearing in a cylindrical portion extending in front of the first sun gear S1.
- the common carrier C1C2 rotates the pinion shaft 11 7 that rotatably supports the long pinion 18 that mates with the first sun gear S1, and the pinion 19 that mates with the second sun gear S2 and the long pinion 18.
- a pion shaft 118 that is supported is supported at both ends.
- the common ring gear R1R2 that meshes with the long pion 18 is directly connected to the third ring gear R3 of the second compound planetary gear 16. That is, the common ring gear R1R2 is fitted to the cylindrical part extending rearward by the flange part snap ring formed in front of the third ring gear R3 of the second compound planetary gear 16 so as to be fitted to the common ring gear.
- a protrusion projecting outward in the radial direction of the flange portion of the third ring gear R3 is engaged with the engagement groove formed in the cylindrical portion of R1R2, and the relative rotation is restricted.
- the third brake B-3 is disposed outside the cylindrical portion extending in front of the first sun gear S1.
- a common spline 119 is engraved in the axial direction on the inner peripheral surface of the central portion in the axial direction of the transmission case body 12a, and the third brake B-3 is formed on the spline formed on the outer peripheral surface of the common spline 119 and the hub member 120.
- a plurality of separator plates and a plurality of friction plates constituting the friction engagement portion 121 are alternately splined.
- the bent portion of the front end of the hub member 120 that is bent radially inward is a flange formed at the front end of the first sun gear S1. It is fixed to the die part by welding or the like.
- the cylinder member 123 is spline-fitted to the common spline 119 with the snap ring 124 restricted from moving forward, and the piston 125 is connected to the cylinder 125 formed on the cylinder member 123.
- a servo chamber 127 is formed between the cylinder 125 and the piston 126 in an oil-tight manner.
- a contact portion protruding forward from the piston 126 faces the separator plate at the rearmost end of the third brake B-3.
- the piston 126 is biased in the direction of separating the separator plate and the friction plate by the spring force of the compression spring 128.
- a port 129 for supplying and discharging hydraulic pressure to the servo chamber 127 is opened in the cylinder member 125.
- the cylinder member 123 is sandwiched between a step portion formed at the rear end portion of the common spline 119 and the snap ring 124 and is restricted from moving in the axial direction.
- a first brake B-1 is disposed outside the first compound planetary gear 15.
- the friction engagement portion 131 of the first brake B-1 is attached to the spline formed on the outer periphery of the spline formed on the inner periphery of the transmission case body 20a and the spline formed on the rear side of the common spline 119.
- a plurality of constituent separator plates and a plurality of friction plates are alternately splined.
- a bent portion that extends forward of the hub member 130 and bends in the radial direction is fixed to the common carrier C1C2 by a bolt 132.
- the hydraulic servo part 133 of the first brake B-1 has a cylinder member 134 fitted in a stepped hole provided in the transmission case body 12a, so that a piston 136 can slide in a cylinder 135 formed in the cylinder member 134.
- the servo chamber 137 is formed in an oil-tight manner between the cylinder 135 and the piston 136.
- a contact portion protruding forward from the piston 136 faces the separator plate at the rearmost end of the first brake B-1.
- the piston 136 is urged in a direction to separate the separator plate and the friction plate by the spring force of the compression spring 138.
- a port 139 for supplying and discharging hydraulic pressure to the servo chamber 137 is opened in the cylinder member 134.
- the second compound planetary gear 16 is disposed on the common axis 13 behind the first compound planetary gear 15.
- the third sun gear S3 of the second compound planetary gear 16 is fitted on the intermediate shaft 54, and the third carrier C3 is spline-fitted with a spline formed on the outer periphery of the rear end of the connecting shaft 77, and is connected to the intermediate shaft 54.
- the connecting member 140 rotatably supported by a dollar bearing is rotatably supported by a cylindrical portion extending in front of the connecting member 140.
- the third carrier C3 is supported at both ends by a pion shaft 141 that rotatably supports the third pion 20 that meshes with the third sun gear S3 and the third ring gear R3.
- a support body 142 is spline-fitted to the inner peripheral surface of the flange portion of the third ring gear R3, and the support body 142 is rotatably supported by a metal bearing on a cylindrical portion protruding in front of the third carrier C3. .
- the inner race 146 of the one-way clutch F-1 is spline-fitted to the outer periphery of the connecting member 140, and the outer race 147 of the one-way clutch F-1 is inserted into a stepped hole formed at the rear of the transmission case body 12a. It is fitted with rotation prevention, and movement in the axial direction is restricted by the snap ring 148 and the stepped portion of the stepped hole.
- the fourth sun gear S4 of the second compound planetary gear 16 is formed on the intermediate shaft 54, and the fourth carrier C4 is coupled to a flange portion formed at the tip of the output shaft 17.
- the fourth carrier C4 is supported at both ends by a pinion shaft 149 that rotatably supports the fourth pinion 21 that meshes with the fourth sun gear S4 and the fourth ring gear R4.
- the fourth ring gear R4 is supported by a spline fitting between a support portion extending outward in the radial direction of the rear end force of the connecting member 140 and a front cylindrical portion, and rearward movement is restricted by a snap ring.
- the second brake B-2 is disposed outside the third ring gear R3.
- a plurality of separator plates constituting the friction engagement portion 150 of the second brake B-2 are formed on the spline formed on the inner peripheral surface of the transmission case body 12a and the spline formed on the outer peripheral surface of the third ring R3.
- a plurality of friction plates are alternately splined.
- the hydraulic servo part 151 of the second brake B-2 is prevented from rotating on the inner peripheral surface of the spline formed in the transmission case body 12a, with the cylinder member 152 being in contact with the outer race 147 and being prevented from moving backward.
- the piston 154 is slidably fitted to a cylinder 153 formed on the cylinder member 152 so that the servo chamber 155 is formed in an oil-tight manner between the cylinder 153 and the piston 154.
- the second brake B-2 via a spring receiver 156 with which the piston 154 is in contact with the front end It faces the separator plate at the rearmost end.
- the piston 154 is urged in a direction to separate the separator plate and the friction plate by the spring force of the compression spring 157 acting on the spring receiver 156.
- the cylinder member 152 has a port 166 that supplies and discharges hydraulic pressure to and from the servo chamber 155.
- a fourth brake B-4 is disposed outside the fourth ring gear R4.
- the blade and the plurality of friction plates are alternately splined.
- the hydraulic servo section 159 of the fourth brake B-4 has a piston 161 slidably fitted to a cylinder 160 formed on the bottom wall 12b of the transmission case body 12a, and a servo between the cylinder 160 and the piston 161.
- the chamber 162 is formed in an oil-tight manner.
- the piston 161 is opposed to the separator plate at the rearmost end of the fourth brake B-4 via the pressing member 163 that is in contact with the front end thereof.
- the piston 161 is biased in the direction of separating the separator plate and the friction plate by the spring force of the compression spring 164.
- An oil passage 165 for supplying and discharging hydraulic pressure to and from the servo chamber 162 is opened in the bottom wall 12b.
- the first compound planetary gear 15 in the second embodiment includes a common sun gear S1S2 rotatably supported on a common axis 13, a long pinion 18 meshing with the common sun gear S1S2,
- the first ring gear R1 meshes directly with the gupine 18 and the second ring gear R2 meshes with the long pione 18 via the pione 19.
- the common sun gear S1S2 of the first compound planetary gear 15 can be connected to the input shaft 14 via the third clutch C-3, and the second ring gear R2 is directly connected to the third ring gear R3 of the second compound planetary gear 16.
- the through-carrier C1C2 can be fixed via the first brake B-1, and the first ring gear R1 can be fixed via the third brake B-3.
- the engagement states of the first to third clutches Cl to C-3, the first to fourth clutches Cl to C-4, and the one-way clutch F-1 at each shift stage are the same as those in the first embodiment of FIG. Is the same.
- the gear ratios ⁇ ⁇ , ⁇ 2, ⁇ 3, and ⁇ 4 of the single-pione planetary gear 26 of the first and second compound planetary gears 15 and 16 and the dub no-repeat planetary gear 27 are set to, for example, 0. 458, 0 440, 0. 394, 0.
- the gear it at each gear is 3.538 at the first speed, 2.060 at the second speed, 1.405 at the third speed, 1.405, at the fourth speed.
- the step between each gear ratio is 1.717 between the 1st and 2nd speed, 1.467 between the 2nd and 3rd speed, 1.127 between the 3rd and 4th speed, 1.127 between the 4th and 5th speed 1. 246, between 5th and 6th speeds 1.275, between 6th and 7th speeds, 1. 099, between 7th and 8th speeds, 1.225, and the gear ratio is appropriate at each gear.
- the gear ratio is appropriate at each gear.
- the elements corresponding to the four vertical lines are arranged in order from the left of the vertical line.
- the elements corresponding to each of the four vertical lines are arranged in order from the left of the vertical line in the fifth, sixth, 7th and 8th elements.
- the common sun gear S1S2 of the first compound planetary gear 15 is the first element
- the second ring gear R2 is the second element
- the common carrier C1C2 is the third element
- the first ring gear R1 is the fourth element
- the third ring gear R3 of the second compound planetary gear 15 is the fifth element
- the third carrier C3 and the fourth ring gear R4 are the sixth element
- the fourth carrier C4 is the seventh element
- the third and fourth sun gears S3 and S4 are the first element. 8 elements.
- the third brake B-3 is made to function as the first brake B-1, and the first brake B-1 Function as the third brake B-3.
- the front carrier of the hub member 120 that constitutes the first brake B-1 (the hub member 120 that constitutes the third brake B-3 in the first embodiment) also has a bent portion that is bent radially inward. Secure to C1C2 with bolts. Outside the first ring gear R1 The bent portion that bends in the radial direction of the hub member 130 of the third brake Bl that is arranged (the hub member 120 that constitutes the first brake Bl in the first embodiment) is fixed to the front end of the first ring gear R1 by welding or the like. To do.
- the third embodiment also differs from the first embodiment in the first compound planetary gear 15, this difference will be described, and the description of other parts will be omitted by assigning the same reference numerals to the same elements.
- the first compound planetary gear 15 in the third embodiment meshes with the first and second sun gears SI and S2 rotatably supported on the common axis 13 and the second sun gear S2.
- the long pinion 18 and the common ring gear R3R4 that meshes with the long pinion 18 via the pinion 19 are configured.
- the second sun gear S2 of the first compound planetary gear 15 can be connected to the input shaft 14 via the third clutch C-3, and the common ring gear R1R2 is directly connected to the third ring gear R3 of the second compound planetary gear 16.
- the common carrier C1C2 can be fixed via the first brake B-1, and the first sun gear S1 can be fixed via the third brake B-3.
- the engagement states of the first to third clutches Cl to C-3, the first to fourth clutches Cl to C-4, and the one-way clutch F-1 at the respective speeds are the same as those in the first embodiment of FIG. It is.
- the gear ratios ⁇ ⁇ , ⁇ 2, ⁇ 3, and ⁇ 4 of the single-pione planetary gear 26 of the first and second compound planetary gears 15 and 16 and the dub no-reply-on planetary gear 27 are set to, for example, 0. 440, 0
- the gear ratio at each gear is 3.538 at the 1st speed, 2.060 at the 2nd speed, 1.365 at the 3rd speed, and 1.365 at the 4th speed. 1.147, 5th speed 1.000, 6th speed 0.849, 7th speed 0.827, 8th speed 0.882, reverse 1st speed 2.904, reverse 2nd speed 1. 855 is an appropriate value.
- the steps between each gear ratio are 1.717 between the 1st and 2nd speed, 1.509 between the 2nd and 3rd speed, 1.191 between the 3rd and 4th speed, and 1191 between the 4th and 5th speed. 1.147, 5th and 6th speeds 1.178, 6th and 7th speeds 1.165, 7th and 8th speeds 1.251, and gear ratio is appropriate at each gear. According to the automatic transmission according to the present embodiment, it is possible to obtain the gear ratios of the 8th forward speed and the 2nd reverse speed that are appropriately separated.
- the elements corresponding to the four vertical lines are arranged in order from the left of the vertical line. 1, 2nd, 3rd, 3rd
- the elements corresponding to the four vertical lines are the fifth, sixth, seventh, and eighth elements in order from the left of the vertical line.
- the second sun gear S2 of the first compound planetary gear 15 is the first element
- the common ring gear R1 R2 is the second element
- the common carrier C1C2 is the third element
- the first sun gear S1 is the fourth element.
- the third ring gear R3 of the second compound planetary gear 15 is the fifth element
- the third carrier C3 and the fourth ring gear R4 are the sixth element
- the fourth carrier C4 is the seventh element
- the third and fourth sun gears S3 and S4 are 8th element.
- the first to third clutches collectively provided in front of the automatic transmission, the single double-pione planetary gear, and the double planetary gear force that also includes two single-pione planetary gear forces are arranged in this order in the axial direction
- the first to fourth brakes that selectively fix each element of the single double beon planetary gear and the double planetary gear are configured to selectively engage the first to third clutches and the first to fourth brakes.
- Japanese Patent Laid-Open No. 2001-263438 discloses an automatic transmission that achieves six forward speeds and one reverse speed.
- the automatic transmission 10 according to the first and second embodiments is an automatic transmission described in Japanese Patent Application Laid-Open No. 2001-263438, in which a single double pion planetary gear is a rabbi type. It is possible to change forward 6th gear to forward 8th gear by simply changing to the double planetary gear of the above, and other components of the automatic transmission of the forward 8-speed and reverse 2-speed automatic transmission according to the present embodiment It can be shared with the components of the automatic transmission in operation.
- the single double beon planetary gear is changed to a rabyo type double planetary gear in addition to the automatic transmission described in Japanese Patent Laid-Open No. 2001-263438.
- the third brake function as the first brake and the first brake function as the third brake
- the sixth forward speed can be changed to the eighth forward speed
- the eighth forward speed according to the second embodiment The other components of the reverse 2nd speed automatic transmission can be shared with the components of the automatic transmission in progress.
- the automatic transmission according to the present invention is used for an automatic transmission that outputs and outputs the rotation of an automobile engine in a plurality of stages by engaging / disengaging a plurality of friction engagement elements including a clutch and a brake. Is suitable.
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Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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CN2007800038473A CN101375085B (zh) | 2006-03-29 | 2007-03-29 | 自动变速器 |
JP2008508590A JP4850239B2 (ja) | 2006-03-29 | 2007-03-29 | 自動変速機 |
DE112007000268T DE112007000268T5 (de) | 2006-03-29 | 2007-03-29 | Automatikgetriebe |
US12/293,737 US7955213B2 (en) | 2006-03-29 | 2007-03-29 | Automatic transmission |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
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JP2006-092488 | 2006-03-29 | ||
JP2006092488 | 2006-03-29 | ||
JP2006-107856 | 2006-04-10 | ||
JP2006107856 | 2006-04-10 |
Publications (1)
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WO2007114215A1 true WO2007114215A1 (ja) | 2007-10-11 |
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Application Number | Title | Priority Date | Filing Date |
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PCT/JP2007/056797 WO2007114216A1 (ja) | 2006-03-29 | 2007-03-29 | 自動変速機 |
PCT/JP2007/056794 WO2007114215A1 (ja) | 2006-03-29 | 2007-03-29 | 自動変速機 |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2007/056797 WO2007114216A1 (ja) | 2006-03-29 | 2007-03-29 | 自動変速機 |
Country Status (4)
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US (2) | US7955214B2 (ja) |
JP (2) | JP4850240B2 (ja) |
DE (2) | DE112007000268T5 (ja) |
WO (2) | WO2007114216A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103415719A (zh) * | 2011-03-30 | 2013-11-27 | 爱信艾达株式会社 | 变速装置 |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7955214B2 (en) * | 2006-03-29 | 2011-06-07 | Aisin Aw Co., Ltd. | Automatic transmission |
US7686730B2 (en) * | 2006-11-09 | 2010-03-30 | Ford Global Technologies, Llc | Multiple speed automatic transmission |
CN101839314B (zh) * | 2009-03-19 | 2012-11-14 | 本田技研工业株式会社 | 装备有行星齿轮机构的自动变速器 |
JP6217270B2 (ja) * | 2013-09-18 | 2017-10-25 | アイシン精機株式会社 | 自動変速機 |
US9528575B2 (en) * | 2015-02-20 | 2016-12-27 | Gm Global Technology Operations, Llc | Multi-speed transmission having a reduction planetary gear set |
US11067169B2 (en) * | 2019-06-10 | 2021-07-20 | GM Global Technology Operations LLC | Automatic transmission turbine shaft with an air bleed for a rotating clutch |
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JPS6065943A (ja) * | 1983-09-20 | 1985-04-15 | Nissan Motor Co Ltd | 変速機の遊星歯車列 |
JP2000046129A (ja) * | 1998-07-28 | 2000-02-18 | Aisin Aw Co Ltd | 車両用自動変速機 |
JP2001263438A (ja) * | 2000-01-11 | 2001-09-26 | Aisin Aw Co Ltd | 車両用自動変速機 |
JP2002213545A (ja) * | 2001-01-19 | 2002-07-31 | Aisin Aw Co Ltd | 自動変速機 |
JP7094856B2 (ja) * | 2018-10-19 | 2022-07-04 | 東京エレクトロン株式会社 | フィルタユニットの調整方法およびプラズマ処理装置 |
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US4711138A (en) | 1985-10-16 | 1987-12-08 | Aisin-Warner Kabushiki Kaisha | Automatic transmission mechanism |
US5518465A (en) * | 1994-11-14 | 1996-05-21 | Hiraiwa; Kazuyoshi | Planetary geartrain |
JP3439315B2 (ja) | 1997-04-04 | 2003-08-25 | アイシン・エィ・ダブリュ株式会社 | 自動変速機 |
JP3712936B2 (ja) * | 2000-11-22 | 2005-11-02 | アイシン・エィ・ダブリュ株式会社 | 自動変速機 |
US6752738B1 (en) * | 2003-05-13 | 2004-06-22 | Daimlerchrysler Corporation | Eight-speed automatic transmission |
US7955214B2 (en) * | 2006-03-29 | 2011-06-07 | Aisin Aw Co., Ltd. | Automatic transmission |
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2007
- 2007-03-29 US US12/293,746 patent/US7955214B2/en not_active Expired - Fee Related
- 2007-03-29 WO PCT/JP2007/056797 patent/WO2007114216A1/ja active Search and Examination
- 2007-03-29 US US12/293,737 patent/US7955213B2/en not_active Expired - Fee Related
- 2007-03-29 DE DE112007000268T patent/DE112007000268T5/de not_active Ceased
- 2007-03-29 WO PCT/JP2007/056794 patent/WO2007114215A1/ja active Search and Examination
- 2007-03-29 JP JP2008508591A patent/JP4850240B2/ja not_active Expired - Fee Related
- 2007-03-29 DE DE112007000261T patent/DE112007000261T5/de not_active Ceased
- 2007-03-29 JP JP2008508590A patent/JP4850239B2/ja not_active Expired - Fee Related
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JPS6065943A (ja) * | 1983-09-20 | 1985-04-15 | Nissan Motor Co Ltd | 変速機の遊星歯車列 |
JP2000046129A (ja) * | 1998-07-28 | 2000-02-18 | Aisin Aw Co Ltd | 車両用自動変速機 |
JP2001263438A (ja) * | 2000-01-11 | 2001-09-26 | Aisin Aw Co Ltd | 車両用自動変速機 |
JP2002213545A (ja) * | 2001-01-19 | 2002-07-31 | Aisin Aw Co Ltd | 自動変速機 |
JP7094856B2 (ja) * | 2018-10-19 | 2022-07-04 | 東京エレクトロン株式会社 | フィルタユニットの調整方法およびプラズマ処理装置 |
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CN103415719A (zh) * | 2011-03-30 | 2013-11-27 | 爱信艾达株式会社 | 变速装置 |
Also Published As
Publication number | Publication date |
---|---|
JP4850239B2 (ja) | 2012-01-11 |
US20100234164A1 (en) | 2010-09-16 |
DE112007000261T5 (de) | 2008-11-20 |
JP4850240B2 (ja) | 2012-01-11 |
DE112007000268T5 (de) | 2008-12-24 |
US7955213B2 (en) | 2011-06-07 |
US20100167866A1 (en) | 2010-07-01 |
US7955214B2 (en) | 2011-06-07 |
JPWO2007114216A1 (ja) | 2009-08-13 |
WO2007114216A1 (ja) | 2007-10-11 |
JPWO2007114215A1 (ja) | 2009-08-13 |
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