WO2007114216A1 - 自動変速機 - Google Patents
自動変速機 Download PDFInfo
- Publication number
- WO2007114216A1 WO2007114216A1 PCT/JP2007/056797 JP2007056797W WO2007114216A1 WO 2007114216 A1 WO2007114216 A1 WO 2007114216A1 JP 2007056797 W JP2007056797 W JP 2007056797W WO 2007114216 A1 WO2007114216 A1 WO 2007114216A1
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- WO
- WIPO (PCT)
- Prior art keywords
- gear
- clutch
- speed
- carrier
- planetary gear
- Prior art date
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 61
- 150000001875 compounds Chemical class 0.000 claims abstract description 146
- 238000010586 diagram Methods 0.000 claims description 35
- 241000920340 Pion Species 0.000 claims description 19
- 230000002093 peripheral effect Effects 0.000 description 34
- 239000002184 metal Substances 0.000 description 8
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 230000009977 dual effect Effects 0.000 description 6
- 238000007599 discharging Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 5
- 238000003466 welding Methods 0.000 description 5
- 238000006243 chemical reaction Methods 0.000 description 4
- 238000001514 detection method Methods 0.000 description 3
- 239000000969 carrier Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- KYKAJFCTULSVSH-UHFFFAOYSA-N chloro(fluoro)methane Chemical compound F[C]Cl KYKAJFCTULSVSH-UHFFFAOYSA-N 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000446 fuel Substances 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.
- Patent Document 1 discloses a double-pin type single planetary gear having a carrier that supports a pair of pinions that mesh with each other, a sun gear that meshes with one of the pair of pinions, and a ring gear that meshes with the other.
- Gear unit front stage and rear stage sun gear, front stage and rear stage ring gear, front stage carrier supporting a pion that meshes with the front stage sun gear and the front stage ring gear, rear stage that supports a pion that meshes with the rear stage sun gear and the rear stage ring gear
- a double planetary gear unit that has a carrier, connects the front and rear sun gears directly, connects the front carrier and the rear ring gear directly on the common axis, directly connects the output shaft to the rear carrier, and directly connects the rotation of the input shaft. Is selectively transmitted to the front and rear sun gears by the first clutch, and the rotation of the input shaft is transmitted to the second carrier and the rear ring gear directly connected to each other by the second clutch.
- the first brake that fixes the carrier of the planetary gear unit, the second brake that fixes the ring gear of the single planetary gear unit and the front ring gear of the double planetary gear unit that are directly connected to each other, and the sun gear of the single planetary gear unit are connected to the one-way clutch.
- a fourth brake for fixing the front stage carrier and the rear stage ring gear directly connected to each other of the double planetary gear unit, and the first, second, third clutch and the first, second,
- An automatic transmission that selectively engages the third and fourth brakes to establish a forward fifth gear and reverse first gear ratio is disclosed.
- Patent Document 2 a common sun gear directly connected to an input shaft is engaged with a first ring gear and a stepped pinion supported by a carrier through a small-diameter pion, and is stepped with a second ring gear.
- the double planetary gear for reduction combined via the large diameter pinion, the sun gear of the first single-pione planetary gear and the sun gear of the second single-pione planetary gear are directly connected, and the carrier of the first single-pione planetary gear and the second single gear
- a second clutch that selectively connects the carrier and the ring gear, a first brake that selectively fixes the first ring gear of the double planetary gear for reduction, and a second ring gear that selectively fixes the second ring gear of the double planetary gear for reduction.
- Double planetary gear for deceleration connected directly to the brake
- a third brake that selectively fixes the ring gear of the first carrier and the first single planetary gear
- a fourth brake that selectively fixes the carrier and the ring gear that are directly connected to the double planetary gear for shifting, and the second single pinion.
- Patent Document 1 Japanese Unexamined Patent Application Publication No. 2002-161951 (Pages 5-8, Fig. 5)
- Patent Document 2 Japanese Patent Laid-Open No. 2002-213545 (Page 5, Figure 1, 2)
- Patent Document 1 The automatic transmission described in Patent Document 1 can smoothly and stably switch the gear ratio between the fifth forward speed and the first reverse speed.
- Patent Document 2 meets such a demand, and can obtain a gear ratio of the eighth forward speed and the reverse speed.
- the automatic transmission disclosed in Patent Document 2 refers to the step ratio between the respective shifts (the low speed side gear).
- Ratio Z high speed side gear ratio forward 1st speed forward 2nd speed "1.638”, forward 2nd speed forward 3rd speed "1.243", forward 3rd speed forward 4 Speed is "1.085", forward 4th speed forward 5th speed “l.509", forward 5th speed forward 6th speed "1.529”, forward 6th speed forward 7th speed But" 1. 053 ", forward 7th speed forward 8th speed is” 1.115 “, especially forward 3rd speed forward 4th speed forward, 6th forward speed Step ratio between 7th forward speed Is less than 1.1.
- a step ratio of less than 1.1 indicates that the gear ratio before and after the gear change does not change much, especially when the gear is changed during the operation. There is a risk that a feeling of shifting (feeling of shifting) will not be obtained for a person, which may give a sense of incongruity.
- the present invention is to provide a small and lightweight automatic transmission that has a gear ratio of eight forward speeds that are appropriately separated and that can provide a sense of speed change in all eight speed stages. .
- the structural feature of the invention according to claim 1 is that the input shaft and four elements sequentially arranged at intervals corresponding to the gear ratio in the speed diagram are arranged in order.
- the first compound planetary gear having corresponding first, second, third and fourth elements, respectively, and four elements sequentially arranged at intervals corresponding to the gear ratio in the speed diagram are arranged in order.
- a second compound planetary gear having corresponding fifth, sixth, seventh, and eighth elements, a second clutch that selectively transmits the rotation of the input shaft to the sixth element, and the rotation of the input shaft.
- the first clutch that selectively transmits to the eight elements, the first brake that selectively fixes the third element, the third brake that selectively fixes the fourth element, and the fifth element A second brake for fixedly fixing, a fourth brake for selectively fixing the sixth element, And an output shaft directly connected to the seventh element, wherein the first compound planetary gear has the first element as the second sun gear and the second element as the second sun gear. And a common ring gear which meshes with the first sun gear via the long pion or the pion, and the long pin which meshes with the third element force. It is a common carrier that rotatably supports the on and the pion, and the fourth element is the first sun gear.
- the structural feature of the invention of claim 2 is that, in claim 1, in the second compound planetary gear, the fifth element is a third ring gear, and the sixth element is A third carrier supporting the third pinion and a fourth ring gear directly connected to the third carrier, wherein the seventh element is a fourth carrier supporting the fourth pinion, and the eighth element is the first carrier.
- 3 rings A third sun gear that meshes with the gear through the third pinion, and a fourth sun gear that is directly coupled with the third sun gear and meshes with the fourth ring gear through the fourth pinion.
- the structural feature of the invention described in claim 3 is that, in claim 2, the intermediate shaft is rotatably supported on a common axis between the input shaft and the output shaft, and the intermediate shaft is The third sun gear and the fourth sun gear can be integrally connected to the input shaft via the first clutch.
- the structural feature of the invention of claim 4 is that in claim 3, a cylindrical connection that is directly connected to the third carrier and that can be connected to the input shaft via the second clutch.
- the connecting shaft is rotatably supported by the intermediate shaft
- the second sun gear is rotatably supported by the connecting shaft
- the first sun gear is rotatably supported by the second sun gear.
- the structural feature of the invention of claim 5 is that, in any one of claims 1 to 4, the third clutch for selectively transmitting the rotation of the input shaft to the first element. It is to prepare.
- the first compound planetary gear includes the first and second sun gears, the long pinion and the common carrier that rotatably supports the pinion, and the long pinion.
- the second compound planetary gear is composed of four elements sequentially arranged at intervals corresponding to the gear ratio in the velocity diagram, and the second and second planetary gears are respectively arranged in order. It consists of 6, 7 and 8 elements.
- the input shaft is selectively connected to the eighth element by the first clutch and selectively connected to the sixth element by the second clutch.
- the common carrier, the common ring gear directly connected to each other, the fifth element, the first sun gear, and the sixth element are selectively fixed by the first to fourth brakes.
- the common ring gear of the first compound planetary gear is arranged side by side with the third brake, so the first ring gear and the second ring gear are arranged side by side with the third brake.
- the overall length can be shortened, and it is possible to provide an automatic transmission that can be small, light, and low in cost and that has a forward 8th gear ratio. .
- step ratio of each gear stage in an automatic transmission having eight forward speeds and two reverse speeds, it is difficult to set the step ratio of each gear stage to an appropriate magnitude due to the large number of gear stages.
- all the step ratios of each gear can be set to an appropriate size, and the engine speed range can be used effectively. Then, the driver can obtain an appropriate shift feeling when shifting in all eight speeds.
- the second compound planetary gear includes a third and a fourth sun gear directly connected to each other and a third and a fourth pinion that rotatably support the third and fourth sun gears, respectively.
- the step ratio of each gear stage can be set to 1.1 or more, that is, an automatic transmission having a simple configuration with eight forward speed stages having a good step ratio can be provided.
- the intermediate shaft that is rotatably supported between the input shaft and the output shaft can be connected to the input shaft via the first clutch. Since the third sun gear and the fourth sun gear of the second compound planetary gear are integrally provided on the intermediate shaft, the third and fourth sun gears directly connected to the second compound planetary gear can be rotated with a simple and compact configuration. Can be transmitted to the 4th sun gear.
- a cylindrical shape that is directly coupled to the third carrier of the second compound planetary gear and that can be coupled to the input shaft via the second clutch.
- the connecting shaft is rotatably supported by the intermediate shaft
- the second sun gear of the first compound planetary gear is rotatably supported by the connecting shaft
- the first sun gear is rotatably supported by the second sun gear.
- the third clutch for selectively transmitting the rotation of the input shaft to the second sun gear is provided, the third clutch is disengaged at the first speed. As a result, it is possible to prevent the first sun gear of the first compound planetary gear from rotating reversely and causing a large relative rotation with the second sun gear.
- the third clutch for selectively transmitting the rotation of the second element (common ring gear) of the first compound planetary gear to the fifth element of the second compound planetary gear Since the third clutch is disengaged at the 1st speed, the 4th element (1st sun gear) of the 1st compound planetary gear rotates in the reverse direction and a large relative rotation with the 1st element (2nd sun gear). Can be prevented.
- 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.
- FIG. 12 is a skeleton diagram showing a fourth embodiment.
- FIG. 13 is a velocity diagram showing a rotation ratio of each element of the planetary gear at each shift speed according to the fourth embodiment.
- FIG. 14 is a skeleton diagram showing a fifth embodiment.
- FIG. 15 is a velocity diagram showing a rotation ratio of each element of the planetary gear at each shift speed according to the fifth embodiment.
- FIG. 16 is a diagram showing an operation table of brakes and clutches at respective gear speeds according to the fifth embodiment.
- FIG. 17 is a skeleton diagram showing the sixth embodiment.
- FIG. 18 is a velocity diagram showing a rotation ratio of each element of the planetary gear at each shift speed according to the sixth embodiment.
- Oil passage 111 ⁇ Distributor, 119 ⁇ Common spline, 120, 130 ⁇ Nove member, 121, 131, 150, 158 ⁇ ⁇ ⁇ Friction engagement portion, 122, 133, 151, 159 ⁇ Hydraulic servo section, 127, 137, 155, 162 ⁇ Servo chamber, 140 ⁇ Connecting member, S1 to S4- "1st to 4th sun gear, C1C2-" common carrier, C3, 4 ⁇ 3rd, 4th carrier, R1R2- “Common ring gear, R3, R4" '3rd, 4th ring gear, C-1 to C-3 ... 1st to 3rd clutch, B-1 to B-4 • "1st to 4th brakes, F-1" "One-way clutch.
- reference numeral 10 denotes an automatic transmission according to the present invention, for example, an automobile engine. It is used to shift the output rotation of the fluid torque converter 11 that is more rotationally driven and transmit it to the 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, a first and a first gear, which are sequentially supported on a common axis 13 in a transmission case 12 attached to the vehicle body. 2, 3rd clutch C-1, C-2, C_3 and 1st, 2nd, 3rd, 4th brake ⁇ -1, ⁇ -2, B-3, B-4, one-way clutch Fl, etc. It is made.
- the first compound planetary gear 15 can rotate 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 is composed of a common carrier C1C2 to be supported and a common ring gear R3R4 that meshes with the first sun gear S1 through the long pinion 18 and meshes with the second sun gear S2 through 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, the third sun gear S3 and the third ring gear R3, which are coupled via the third pinion 20, and the fourth sun gear S4 and the fourth pinion 21, which are meshed with the third carrier C3. And a fourth ring gear R4 directly connected to 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 sun gear speed Ns, the carrier speed Nc, the ring gear speed Nr and the gear ratio of the single ruby-on planetary gear The relationship between the gears is given by equation (1).
- the relationship between the sun gear rotation speed Ns, the carrier rotation speed Nc, the ring gear rotation speed Nr and the gear ratio of the double beon planetary gear is The gear ratio at each gear stage is calculated based on the equations (1) and (2).
- 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 (l +) Nc—E Ns '.' (L)
- Nr (1—E) Nc + Ns' ⁇ ⁇ (2)
- the first and second compound planetary gears 15 , 16 speed ratio of each element Is the velocity diagram shown in Fig. 3.
- the velocity 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.
- the velocity diagrams of the first and second compound planetary gears 15 and 16 are shown 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-pione planetary gear 26 and the double-pione planetary gear 27 are shared. , C2 and Rl, R2 are attached to each vertical line, and the speed ratio of common carrier C1C2 and common ring gear R1R2 is shown.
- the third and fourth sun gears S3 and S4 of the single pion 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, R4
- the speed ratios of the third and fourth sun gears S3 and S4, the third carrier C3 and the fourth ring gear R4 are shown on each vertical line marked with.
- 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 R1 R2 is the common carrier.
- Vertical line force of C1C2 It is arranged on the opposite side of the vertical line of sun gear S1 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 R1R2 is the vertical line force of common carrier C1C2.
- each interval 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 separated from the vertical lines of the third and fourth carriers C3 and C4 on the opposite side of the vertical lines of the third and fourth sun gears S3 and S4, respectively.
- the speed diagram shows that the first to third clutches C-1 to C-3, the first to fourth brakes ⁇ -1 to ⁇ -4, and the one-way clutch F-1 were selectively activated. 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 each of the four vertical lines are the vertical lines.
- the fifth, sixth, seventh, and eighth elements are arranged in order from the left.
- 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 ring gear R4 are connected to the one-way clutch F-1. Therefore, the reverse rotation is prevented and the reaction force is received, so that the fourth carrier C4 and the output shaft 17 are decelerated at the gear ratio of the first speed and rotated forward.
- Second speed (2nd) is achieved by engagement of first clutch C-1 and 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 and 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 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 and third clutches C-l and 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 C-l 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 reached by engagement of the second and third clutches C-2 and C-3 and the third brake B-3. Made.
- 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 common 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 second clutch C-2 and 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 third clutch C-3 and first 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 common carrier C1C2 is fixed via the first 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.
- Second reverse speed (Rev2) is achieved by engagement of third clutch C-3 and third and fourth brakes B-3 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 first sun gear S1 is fixed via the third brake B-3.
- Common ring gear R1R2 is connected to third ring gear R3 of second compound planetary gear 16 directly connected to third carrier C3 and fourth ring gear R4 connected directly Since it is fixed via 4 brakes B-4, the 4th carrier C4 and the output shaft 17 are decelerated at the gear ratio of the reverse 2nd speed and reversely rotated.
- Gear ratios of the first and second compound planetary gears 15 and 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 main body 12a and a rear case 12b fixed to the bottom of the transmission case main body 12 with bolts 44.
- a front wall member 43 is formed on the front end surface of the transmission case main body 12a. It is fixed with bolts 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, and the stator shaft 50 is press-fitted and fixed to the inner peripheral surface of the boss portion 43a. However, it is supported by a single dollar bearing 51 and a metal bearing 52 so as to be rotatable around the 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 rotatably supported coaxially by a shaft bearing 55 in the shaft bearing hole 53.
- 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-car bearing 62 which is connected to an unillustrated engine output shaft and is provided with a pump impeller 22 of a fluid torque comparator 11 inside. ing.
- 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 arranged in parallel in front of the first compound planetary gear 15 at the front portion of the transmission case 12.
- the boss portion 43a of the front wall member 43 has a base end portion 65a of a common clutch drum 65 shared by the second and third clutches C-2 and C_3, which can be rotated by a single dollar bearing 66 and a thrust bearing 67. It is supported.
- the common clutch drum 65 is spline-fitted to the outer peripheral surface of the input shaft 14 on 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.
- the common clutch drum 65 has a bottom wall 65b projecting radially from a base end portion 65a, and a cylindrical portion 65c extending rearward from the outer periphery of the bottom wall 65b.
- the second and third hub members 68 and 69 are also sequentially arranged on the inner periphery of the cylindrical portion 65c, and the forward force is also sequentially arranged, and the inner peripheral surface of the cylindrical portion 65c of the common clutch drum 65 and the second and third hub members 68 and 69
- 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 cylindrical portions 68a and 69a.
- the spline is engaged.
- the second hub member 68 is bent backward in the radial direction. It is bent and fixed to the flange portion formed at the front end of a cylindrical connecting shaft 77 supported by a metal bearing 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 double 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 in front of the first sun gear S1 of the first compound planetary gear 15.
- the outer peripheral surface of the cylindrical portion extending in front of the sun gear S2 is spline-fitted.
- 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.
- a compression spring 91 is interposed between the cancel plate 90 and the rear surface of the piston 88 to urge the separator plate 72 and the friction plate 74 in the non-coupling direction, and the centrifugal force generated in the servo chamber 89 is interposed therebetween.
- a cancellation chamber 92 is provided to cancel the hydraulic pressure! 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. Oilway 110 force The boss 43a 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 to the boss portion 43a via a hydraulic servo valve (not shown). The oil passage is communicated with the discharge port of the oil pump 45 through the oil passage 112 formed in the oil pump.
- the hydraulic servo section 93 of the third clutch C-3 is slidably fitted to the front outer peripheral surface of the base end 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.
- 2nd and And hydraulic servos 86 and 93 of the 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. The abutting portion protruding rearward from the piston 102 faces the foremost separator plate 83 of the first clutch C-1.
- 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). Oil through 112 Connected to the discharge port of pump 45.
- 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 cylindrical connecting shaft 77 that is directly connected to the third carrier C3 of the second compound planetary gear 16 and that can be connected to the input shaft 14 via the second clutch C-2 is the intermediate shaft 54.
- the second sun gear S2 of the first compound planetary gear 15 is rotatably supported by the connecting shaft 77, and the first sun gear S1 is rotatably supported by the second sun gear S2.
- the rotation of the shaft 14 can be transmitted to the third carrier C3 via the second clutch C-2 with a simple configuration, and the first and second sun gears SI and S2 are arranged in a compact manner along the axial direction. Can do.
- the first A third brake B-3 that can fix the sun gear SI is arranged in front of the common ring gear R1R2 in the axial direction.
- a common spline 119 is carved in the axial direction on the inner peripheral surface of the central portion of the transmission case body 12a, and the third brake B-3 is frictionally engaged with the spline formed on the outer peripheral surface of the common spline 119 and the hub member 120.
- the plurality of separator plates and the plurality of friction plates constituting the part 121 are alternately splined.
- a bent portion where the front end of the knob member 120 is also bent radially inward is fixed to a flange portion formed at the front end of the first sun gear S1 by welding or the like.
- the cylinder member 123 is spline-fitted to the common spline 119, and the piston 126 is slidably fitted to the cylinder 125 formed on the cylinder part 123.
- a servo chamber 127 is formed between the piston 5 and the piston 126 in an oil-tight manner.
- a contact portion protruding forward from the piston 126 faces the separator blade 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 plurality of separator plates and the plurality of friction plates constituting the friction engagement portion 131 of the first brake B-1 are alternately spline-engaged with the splines formed on the outer peripheral surfaces of the common spline 119 and the hub member 130.
- RU 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 cylinder member 134 is fitted in a stepped hole provided in the transmission case body 12a, and the piston 136 slides on the 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 part protruding forward from the piston 136 faces the separator plate at the rearmost end of the first brake B-1.
- Piston 136 is seized by the spring force of compression spring 138. It is urged in a direction to separate the palator plate and the friction plate.
- 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 outer 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 intermediate shaft 54 rotatably supported on the common axis between the input shaft 14 and the output shaft 17 by the transmission case 12 is connected to the input shaft 14 via the first clutch C-1. Since the third sun gear S3 and the fourth sun gear S4 of the second compound planetary gear 16 are provided on the intermediate shaft 54 in a body-like manner, the input shaft 14 can be connected with a simple and compact configuration. The rotation can be transmitted to the third and fourth sun gears S3 and S4 directly connected to the second compound planetary gear 16.
- 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 piston 154 is opposed to the separator plate at the rearmost end of the second brake B-2 via a spring receiver 156 abutted on the front 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. Hydraulic pressure is supplied into the servo chamber 162 and the piston 161 moves forward. When moved, the piston 161 presses the separator plate at the rearmost end via the pressing member 163, and presses the separator plate and the friction plate to engage the fourth brake B-4.
- the first compound planetary gear 15 in the second embodiment is a pinion that meshes with the first and second sun gears SI and S2 that are rotatably supported on a common axis 13 respectively.
- the common carrier C1C2 that rotatably supports the long pinion 18 through the first sun gear S1 and the pinion 19, and the second sun gear S2, the pinion 19 and the long pinion 18 It is composed of a common ring gear R3R4.
- 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 C-1 to C-3, the first to fourth clutches Cl to C-4, and the one-way clutch F-1 at each gear position are the same as in the first embodiment of FIG. Is the same.
- the gear ratios ⁇ ⁇ , ⁇ 2, ⁇ 3, and ⁇ 4 of the first and second single planetary gears 15 and 16 and the dub no-repeller 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 16 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 automatic transmission according to the present embodiment in which the common ring gear R1R2 of the first compound planetary gear is arranged in the axial direction in the vicinity of the inner peripheral wall surface of the transmission case 12 with the third brake B-3.
- the total length of the automatic transmission can be shortened, and it is possible to reduce the size, weight, and cost. .
- the third embodiment Since the third embodiment is different from the first embodiment only in the elements that can be connected by the third clutch C-3, this difference will be described, and the other parts are the same as the same elements. A reference number is attached and explanation is omitted.
- the second sanghi S2 of the first compound planetary gear 15 is directly connected to the input shaft 14, and the common ring gear R1R2 is connected to the second compound system via the third clutch C-3. It can be connected to the third ring gear R3 of the planetary gear 16.
- the velocity diagrams of the first and second compound planetary gears 15 and 16 are substantially the same as those of the first embodiment except for the elements connected to the third clutch C-3, as shown in FIG. is there. Since the common ring gear R1R2 of the first compound planetary gear 15 and the third ring gear R3 of the second compound planetary gear 16 are selectively coupled by the third clutch C-3, the third clutch C-3 is engaged. R1R2 in the speed diagram of the 1st and 2nd compound planetary gears 15 and 16 shown side by side on the left and right in Fig.
- the first to third clutches Cl to C-3 and the first to fourth brakes ⁇ -1 to ⁇ -4 are shown in the operation table of FIG. So as to selectively engage before It can achieve 8 forward speeds and 2 reverse speeds.
- the rotation of the input shaft 14 is input to the third and fourth sun gears S3, S4 directly connected to the second compound planetary gear 16 via the first clutch C-1, and is directly connected. Since the third carrier C3 and the fourth ring gear R4 are prevented from reversing by the one-way clutch F-1, the fourth carrier C4 and the output shaft 17 are decelerated at the gear ratio of the first speed. To rotate forward.
- the rotation of the input shaft 14 is directly input to the second sun gear S2 of the first compound planetary gear 15, and the common carrier C1C2 is fixed via the first brake B-1.
- the rotational force of the common ring gear R1R2 that has reduced the rotation of the input shaft 14 is transmitted to the third ring gear R3 of the dual planetary gear 16 via the third clutch C-3, and the rotation of the input shaft 14 is transmitted to the third planetary gear 16 Since it is input to the third and fourth sun gears 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 third speed and are rotated forward.
- the rotation of the input shaft 14 is directly input to the second sun gear S2 of the first compound planetary gear 15, and the first sun gear S1 is fixed via the third brake B-3.
- the rotational force of the common ring gear R1R2 that reduced the rotation of the input shaft 14 is transmitted to the third ring gear R3 of the double planetary gear 16 via the third clutch C-3, and the rotation of the input shaft 14 is transmitted to the third ring gear 16 of the double planetary gear 16.
- the fourth sun gears S 3 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 rotation of the input shaft 14 is directly input to the second sun gear S2 of the first compound planetary gear 15, and the common carrier C1C2 is fixed via the first brake B-1.
- the rotational force of the common ring gear R1R2 that reduced the rotation of the input shaft 14 is transmitted to the third ring gear R3 of the second compound planetary gear 16 via the third clutch C-3 and directly connected to the third carrier C3 and the second carrier C3.
- the 4-ring gear R4 is coupled to the input shaft 14 via the second 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 rotation of the input shaft 14 is input to the third carrier C3 and the fourth ring gear R4, which are directly connected to the second compound planetary gear 16, via the second clutch C-2. Since the ring gear R3 is fixed by the second brake B-2, 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 rotation of the input shaft 14 is directly input to the second sun gear S2 of the first compound planetary gear 15, and the common carrier C1C2 is fixed via the first brake B-1.
- the rotational force of the common ring gear R1R2 that reduced the rotation of the input shaft 14 is transmitted to the third ring gear R3 of the second compound planetary gear 16 via the third clutch C-3 and directly connected to the third carrier C3 and the fourth carrier C3. Since the ring gear R4 is fixed via the fourth brake B-4, the fourth carrier C4 and the output shaft 17 are decelerated at the gear ratio of the reverse first speed and reversely rotated.
- the fourth embodiment differs from the second embodiment only in the elements that can be connected by the third clutch C-3, so this difference will be described, and the other parts are the same as the same elements. A reference number is attached and explanation is omitted.
- the second sanghi S2 of the first compound planetary gear 15 is directly connected to the input shaft 14, and the common ring gear R1R2 is connected to the second compound system via the third clutch C-3. It can be connected to the third ring gear R3 of the planetary gear 16.
- the velocity diagrams of the first and second compound planetary gears 15 and 16 are substantially the same as those of the second embodiment except for the elements connected to the third clutch C-3, as shown in FIG. is there. Since the common ring gear R1R2 of the first compound planetary gear 15 and the third ring gear R3 of the second compound planetary gear 16 are selectively coupled by the third clutch C-3, the third clutch C-3 is engaged. R1R2 in the speed diagrams of the 1st and 2nd compound planetary gears 15 and 16 listed side by side on the left and right in Fig.
- the first to third clutches Cl to C-3 and the first to fourth brakes ⁇ -1 to ⁇ -4 are shown in the operation table of FIG. By selectively engaging, it is possible to achieve 8 forward speeds and 2 reverse speeds.
- the fifth embodiment is different from the first embodiment only in that the second sun gear S2 of the first compound planetary gear 15 without the third clutch C-3 is directly connected to the input shaft 14.
- the different parts will be described, and the other parts will be given the same reference numerals and the description thereof will be omitted.
- the second sun gear S2 of the first compound planetary gear 15 is connected to the input shaft.
- the common ring gear R1R2 of the first compound planetary gear 15 is directly coupled to the third ring gear R3 of the second compound planetary gear 16.
- the speed diagrams of the first and second compound planetary gears 15 and 16 are the same as those shown in FIG. 15, except that the speed ratio of the second sun gear S2 of the first compound planetary gear 15 is always 1. It is almost the same as the embodiment.
- the first and second clutches Cl and C_2 and the first to fourth brakes ⁇ ⁇ ⁇ ⁇ -1 to ⁇ -4 are as shown in the operation table of FIG. Selectively engage to achieve 8 forward speeds and 2 reverse speeds.
- the rotation of the input shaft 14 is input to the third and fourth sun gears S3 and S4 directly connected to the second compound planetary gear 16 via the first clutch C-1 and directly connected. Since the third carrier C3 and the fourth ring gear R4 are prevented from reversing by the one-way clutch F-1, the fourth carrier C4 and the output shaft 17 are decelerated at the gear ratio of the first speed. To rotate forward. When the engine brake is applied, the directly connected third carrier C3 and fourth ring gear R4 are fixed by engagement of the fourth brake B-4.
- the rotation of the input shaft 14 is input to the third and fourth sun gears S3 and S4 directly connected to the second compound planetary gear 16 via the first clutch C-1, and the third Since the ring gear R3 is fixed by the second brake B-2, the fourth carrier C4 and the output shaft 17 are decelerated at the gear ratio of the second speed and rotated forward.
- the rotation of the input shaft 14 is input to the third carrier C3 and the fourth ring gear R4, which are directly connected to the second compound planetary gear 16, via the second clutch C-2. Since the ring gear R3 is fixed by the second brake B-2, 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 rotation of the input shaft 14 is the second sun of the first compound planetary gear 15. Directly input to gear S2, and common carrier C1C2 is fixed via first brake B-1.
- the rotation force of common ring gear R1R2 that reduces the rotation of input shaft 14 is the second directly connected to common ring gear R1R2. Since the third carrier C3 and the fourth ring gear R4, which are transmitted to the third ring gear R3 of the double planetary gear 16 and directly connected thereto, are fixed via the fourth brake B-4, the fourth carrier C4 extends to the output shaft 17 Is decelerated at the gear ratio of reverse 1st speed and reversely rotated.
- the sixth embodiment is different from the second embodiment only in that the second sun gear S2 of the first compound planetary gear 15 that is not provided with the third clutch C-3 is directly connected to the input shaft 14. Therefore, this different part will be described, and for the other parts, the same reference numerals will be assigned to the same elements and description thereof will be omitted.
- the second sun gear S2 of the first compound planetary gear 15 is directly connected to the input shaft 14, and the common ring gear R1R2 of the first compound planetary gear 15 is connected to the second compound planetary gear 16. Is directly connected to the third ring gear R3.
- the speed diagrams of the first and second compound planetary gears 15 and 16 are as shown in Fig. 18, except that the speed ratio of the second sun gear S2 of the first compound planetary gear 15 is always 1. It is almost the same as the embodiment. Also in the automatic transmission 10 according to the sixth embodiment, the first and second clutches C-1 and C-2 and the first to fourth brakes ⁇ -1 to ⁇ -4 are shown in the operation table of FIG. Can be selectively engaged to achieve 8 forward speeds and 2 reverse speeds.
- the second sun gear S2 of the first compound planetary gear 15 is directly connected to the input shaft 14, and the common ring gear R1R2 of the first compound planetary gear 15 is connected to the third compound gear 16 of the second compound planetary gear 16. Since the third clutch C-3 is not directly connected to the ring gear R3, The speed machine 10 can be reduced in size and weight to reduce the cost.
- the automatic transmission according to the present invention is suitable for use in an automatic transmission that outputs and outputs the rotation of an automobile engine in a plurality of stages by engaging and disengaging a plurality of friction engagement elements including a clutch and a brake. .
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN2007800037841A CN101375084B (zh) | 2006-03-29 | 2007-03-29 | 自动变速器 |
JP2008508591A JP4850240B2 (ja) | 2006-03-29 | 2007-03-29 | 自動変速機 |
DE112007000261T DE112007000261T5 (de) | 2006-03-29 | 2007-03-29 | Automatikgetriebe |
US12/293,746 US7955214B2 (en) | 2006-03-29 | 2007-03-29 | Automatic transmission |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006-092488 | 2006-03-29 | ||
JP2006092488 | 2006-03-29 | ||
JP2006-107856 | 2006-04-10 | ||
JP2006107856 | 2006-04-10 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007114216A1 true WO2007114216A1 (ja) | 2007-10-11 |
Family
ID=38563484
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
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 After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2007/056794 WO2007114215A1 (ja) | 2006-03-29 | 2007-03-29 | 自動変速機 |
Country Status (4)
Country | Link |
---|---|
US (2) | US7955214B2 (ja) |
JP (2) | JP4850240B2 (ja) |
DE (2) | DE112007000268T5 (ja) |
WO (2) | WO2007114216A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101839314A (zh) * | 2009-03-19 | 2010-09-22 | 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 |
GB2443720B (en) * | 2006-11-09 | 2011-03-23 | Ford Global Tech Llc | Multiple speed automatic transmission |
JP2015059606A (ja) * | 2013-09-18 | 2015-03-30 | アイシン精機株式会社 | 自動変速機 |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7955214B2 (en) * | 2006-03-29 | 2011-06-07 | Aisin Aw Co., Ltd. | Automatic transmission |
JP5585566B2 (ja) * | 2011-03-30 | 2014-09-10 | アイシン・エィ・ダブリュ株式会社 | 変速装置 |
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 |
Citations (4)
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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 |
JPH10281239A (ja) * | 1997-04-04 | 1998-10-23 | Aisin Aw Co Ltd | 自動変速機 |
JP2000046129A (ja) * | 1998-07-28 | 2000-02-18 | Aisin Aw Co Ltd | 車両用自動変速機 |
JP2002161951A (ja) * | 2000-11-22 | 2002-06-07 | Aisin Aw Co Ltd | 自動変速機 |
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US4660439A (en) * | 1983-09-08 | 1987-04-28 | Nissan Motor Co., Ltd. | Planetary gear train for automatic transmission |
JPH0794856B2 (ja) * | 1985-12-16 | 1995-10-11 | アイシン・エィ・ダブリュ株式会社 | 自動変速機におけるクラツチ装置 |
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 |
JP3463274B2 (ja) | 2000-01-11 | 2003-11-05 | アイシン・エィ・ダブリュ株式会社 | 車両用自動変速機 |
JP4590742B2 (ja) | 2001-01-19 | 2010-12-01 | 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 |
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 |
-
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
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6065943A (ja) * | 1983-09-20 | 1985-04-15 | Nissan Motor Co Ltd | 変速機の遊星歯車列 |
JPH10281239A (ja) * | 1997-04-04 | 1998-10-23 | Aisin Aw Co Ltd | 自動変速機 |
JP2000046129A (ja) * | 1998-07-28 | 2000-02-18 | Aisin Aw Co Ltd | 車両用自動変速機 |
JP2002161951A (ja) * | 2000-11-22 | 2002-06-07 | Aisin Aw Co Ltd | 自動変速機 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2443720B (en) * | 2006-11-09 | 2011-03-23 | Ford Global Tech Llc | Multiple speed automatic transmission |
CN101839314A (zh) * | 2009-03-19 | 2010-09-22 | 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 |
JP2015059606A (ja) * | 2013-09-18 | 2015-03-30 | アイシン精機株式会社 | 自動変速機 |
Also Published As
Publication number | Publication date |
---|---|
JP4850239B2 (ja) | 2012-01-11 |
WO2007114215A1 (ja) | 2007-10-11 |
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 |
JPWO2007114215A1 (ja) | 2009-08-13 |
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