WO2016063857A1 - 自動変速機 - Google Patents
自動変速機 Download PDFInfo
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- WO2016063857A1 WO2016063857A1 PCT/JP2015/079530 JP2015079530W WO2016063857A1 WO 2016063857 A1 WO2016063857 A1 WO 2016063857A1 JP 2015079530 W JP2015079530 W JP 2015079530W WO 2016063857 A1 WO2016063857 A1 WO 2016063857A1
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- clutch
- brake
- sun gear
- engaged
- gear
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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
- F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/082—Planet carriers
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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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/10—Braking arrangements
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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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H2057/087—Arrangement and support of friction devices in planetary gearings, e.g. support of clutch drums, stacked arrangements of friction devices
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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
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine 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
- F16H2200/20—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
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four 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
- F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2064—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using at least one positive clutch, e.g. dog clutch
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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
- F16H2200/2094—Transmissions using gears with orbital motion using positive clutches, e.g. dog clutches
Definitions
- the present invention relates to an automatic transmission mounted on a vehicle, and belongs to the technical field of vehicle transmissions.
- An automatic transmission mounted on a vehicle generally includes a plurality of planetary gear sets and a plurality of hydraulic friction engagement elements such as clutches and brakes, and by selectively fastening these friction engagement elements by hydraulic control, By switching the power transmission path through each planetary gear set, it is possible to realize a plurality of forward shift speeds and typically one reverse speed, but in recent years it has improved the running performance, For the purpose of improving fuel efficiency performance or reducing power consumption of the driving motor, there is a tendency that the shift speed is increased.
- Patent Document 1 includes three planetary gear sets PG11, PG12, and PG13, four clutches CL11, CL12, CL13, and CL14, and two brakes BR11 and BR12, as shown in FIG.
- an automatic transmission that realizes nine forward speeds and one reverse speed by engaging any two of the brakes and the brake is disclosed.
- the automatic transmission described in Patent Document 1 is a horizontal type used for FF vehicles (front engine / front drive vehicle) and the like, and is mounted in a posture in which the shaft center faces the vehicle width direction. Power from a power source such as an engine or a motor is input from an input shaft A disposed on the shaft center, and power via a speed change mechanism such as a planetary gear set or a clutch is transmitted to the carrier of the third planetary gear set PG13. The signal is output from an output section B provided in C13 to a shaft (not shown) arranged in parallel to the input shaft A via a gear or the like.
- a horizontal automatic transmission can be used in an FR vehicle (front engine / rear drive vehicle) or the like without changing the structure of the transmission mechanism, that is, an input shaft and an output shaft. May be considered to be changed to an automatic transmission arranged on the same axis in the vehicle longitudinal direction.
- the output portion B is disposed between the third planetary gear set PG13 and the second brake BR12, and the third planetary gear is disposed on the inner peripheral side of the output portion B. Since there is a connecting member C that connects the sun gear S13 of the set PG13 and the second brake BR12, in this configuration, the output portion B can be connected to the output shaft arranged on the same axis as the input shaft A. Can not.
- the third planetary gear set PG13 is a double sun gear type in which the sun gear is divided into first and second sun gears S131 and S132 arranged in the axial direction. If an output part B ′ that passes between the second sun gears S131 and S132 and extends radially inward is provided, it can be connected to an output shaft D arranged on the same axis as the input shaft. . This makes it possible to change the horizontal automatic transmission to the vertical automatic transmission without significantly changing the configuration of the transmission mechanism.
- the output shaft D penetrates the inside of one divided sun gear S132 in the third planetary gear set PG13.
- the output shaft D needs to have a diameter larger than that of the input shaft A in order to transmit torque whose input torque is increased by an amount corresponding to the maximum reduction ratio. Therefore, the diameter of the sun gear S132 also increases, and accordingly, the overall diameter of the third planetary gear PG13 increases.
- the increase in the diameter of the third planetary gear PG13 as described above causes an increase in the radial dimension of the end portion on the output side of the automatic transmission.
- the width direction dimensions of the driver's seat and the passenger seat in the vehicle interior are restricted, and the comfortability deteriorates. There is a fear.
- Such a problem is a problem common to a vertical automatic transmission in which a planetary gear set is disposed on an output shaft having a relatively large diameter regardless of the number of shift stages and other configurations.
- the present invention has been made in view of the above-described situation regarding the automatic transmission, and an object thereof is to realize a compact vertical automatic transmission capable of reducing the radial dimension of the end portion on the output side. .
- An automatic transmission according to the present invention for solving the above problems includes an input shaft coupled to a drive source, an output shaft disposed on the same axis as the input shaft on the side opposite to the drive shaft of the input shaft, A first planetary gear set having a first sun gear, a first carrier, and a first ring gear; and a second sun gear, a second carrier, and a first planetary gear set disposed on a side opposite to the driving source of the first planetary gear set; A second planetary gear set having a second ring gear, a first brake disposed on the drive source side of the first planetary gear set, and the first and second planetary gear sets and the first brake are accommodated therein.
- a transmission case is provided to a drive source, an output shaft disposed on the same axis as the input shaft on the side opposite to the drive shaft of the input shaft, A first planetary gear set having a first sun gear, a first carrier, and a first ring gear; and a second sun gear, a second carrier, and a first planetary
- the first sun gear has a first split sun gear on the drive source side and a second split sun gear on the counter drive source side, and the first split sun gear is connected to the first brake and the first split sun gear.
- the second split sun gear is always connected to the second sun gear, and the input shaft is connected to the inside of the first split sun gear and the first and second split gears.
- the first shaft is always connected to the first carrier through the sun gear, and the output shaft is always connected to the second carrier.
- the radial dimension of the output side end of the automatic transmission can be reduced.
- FIG. 1 is a cross-sectional view of an automatic transmission according to a first embodiment of the present invention.
- 1 is a skeleton diagram of an automatic transmission according to a first embodiment. It is a fastening table
- FIG. 10 is a schematic diagram of an automatic transmission according to a fourth embodiment of the present invention.
- FIG. 10 is a schematic diagram of an automatic transmission according to a fourth embodiment of the present invention.
- FIG. 10 is a schematic diagram of an automatic transmission according to a fifth embodiment of the present invention. It is a fastening table
- FIG. 10 is a skeleton diagram showing a conventional example of a horizontal automatic transmission having nine forward speeds.
- FIG. 12 is a skeleton diagram showing the automatic transmission of FIG. 11 changed to a vertical installation type.
- FIG. 1 and 2 are a cross-sectional view and a skeleton diagram showing a configuration of the automatic transmission 10 according to the first embodiment of the present invention.
- This automatic transmission 10 is a vertical automatic transmission mounted on a vehicle such as an FR vehicle, and is inserted into the transmission case 11 from a transmission case 11 and a drive source (left side in the figure) of the vehicle. And an output shaft 13 that protrudes from the inside of the transmission case 11 to the opposite drive source side (right side in the figure).
- the input shaft 12 and the output shaft 13 are arranged on the same axial center along the vehicle longitudinal direction, and are in a vertically installed posture in which the input shaft 12 is located on the vehicle front side and the output shaft 13 is located on the vehicle rear side.
- An automatic transmission 10 is provided. Therefore, hereinafter, the drive source side (left side in the figure) is sometimes referred to as the front side, and the counter drive source side (right side in the figure) is sometimes referred to as the rear side.
- the first, second, third, and fourth planetary gear sets (hereinafter simply referred to as “gear sets”) PG1, PG2, PG3, and PG4 are on the front side (drive source side). Are arranged in order.
- a first clutch CL1 is disposed in front of the first gear set PG1 in the transmission case 11, a second clutch CL2 is disposed in front of the first clutch CL1, and a third clutch is disposed in front of the second clutch CL2.
- a clutch CL3 is provided.
- a first brake BR1 is disposed on the front side of the third clutch CL3, and a second brake BR2 is disposed on the radially outer side of the third gear set PG3.
- the frictional engagement elements (the first to third clutches CL1 to CL3 and the first and second brakes BR1 and BR2) of the automatic transmission 10 are connected to the first brake BR1 and the third brake from the front side (drive source side).
- the clutch CL3, the second clutch CL2, the first clutch CL1, and the second brake BR2 are arranged in the axial direction in this order.
- the first to fourth gear sets PG1 to PG4 are all single pinion types in which the pinion supported by the carrier is directly meshed with the sun gear and the ring gear.
- the first gear set PG1 includes a first sun gear S1, a first ring gear R1, and a first carrier C1 as rotating elements.
- the second gear set PG2 includes a second sun gear S2, a second ring gear R2, and a second carrier C2 as rotational elements.
- the third gear set PG3 includes a third sun gear S3, a third ring gear R3, and a third carrier C3 as rotational elements.
- the fourth gear set PG4 includes a fourth sun gear S4, a fourth ring gear R4, and a fourth carrier C4 as rotational elements.
- the first gear set PG1 is a double sun gear type in which the first sun gear S1 is divided into two in the axial direction. That is, the first sun gear S1 includes a front first sun gear S1a disposed on the front side in the axial direction and a rear first sun gear S1b disposed on the rear side. Since the pair of first sun gears S1a and S1b have the same number of teeth and mesh with the same pinion supported by the first carrier C1, the rotation speeds of the first sun gears S1a and S1b are always equal. That is, the pair of front and rear first sun gears S1a and S1b always rotate at the same speed, and when one rotation stops, the other rotation also stops.
- the first sun gear S1 (more specifically, the rear first sun gear S1b) and the fourth sun gear S4 are always connected, the first ring gear R1 and the second sun gear S2 are always connected, The second carrier C2 and the fourth carrier C4 are always connected, and the third carrier C3 and the fourth ring gear R4 are always connected.
- the input shaft 12 is always connected to the first carrier C1, and the output shaft 13 is always connected to the fourth carrier C4.
- the input shaft 12 is coupled to the first carrier C1 via a power transmission member 18 that passes between a pair of front and rear first sun gears S1a and S1b.
- the rear first sun gear S1b and the fourth sun gear S4 are connected to each other through the power transmission member 15.
- the fourth carrier C4 and the second carrier C2 are connected to each other via the power transmission member 16.
- the first clutch CL1 connects and disconnects the input shaft 12, the first carrier C1, and the third sun gear S3.
- the second clutch CL2 connects and disconnects the first ring gear R1, the second sun gear S2, and the third sun gear S3.
- the third clutch CL3 connects and disconnects the second ring gear R2 and the third sun gear S3.
- the first clutch CL1 transmits power to the rotatable inner holding member coupled to the first carrier C1, the hub-side friction plate engaged with the outer peripheral surface of the inner holding member, and the third sun gear S3.
- the drum side friction plate engaged with the inner peripheral surface of the outer holding member, the hub side friction plate and the drum side friction plate.
- a piston P1 that is driven back and forth in the axial direction.
- a hydraulic chamber F1 into which hydraulic pressure supplied from the valve body VB (FIG. 1) is introduced is defined at a position adjacent to the piston P1, and the hub side according to the supply and discharge of hydraulic pressure to the hydraulic chamber F1 is defined.
- the friction plate and the drum side friction plate are pressed or released.
- the inner holding member and the outer holding member are connected or separated from each other by the pressure contact or pressure release, and accordingly, the input shaft 12, the first carrier C1, and the third sun gear S3 are connected or disconnected.
- the second clutch CL2 includes a rotatable inner holding member coupled to the third sun gear S3 via power transmission members 5 and 8, a hub side friction plate engaged with the outer peripheral surface of the inner holding member, A rotatable outer holding member coupled to the ring gear R1 and the second sun gear S2 via a power transmission member 7, a drum side friction plate engaged with an inner peripheral surface of the outer holding member, a hub side friction plate and a drum It has a piston P2 that is driven back and forth in the axial direction to press-contact the side friction plate.
- a hydraulic chamber F2 into which the hydraulic pressure supplied from the valve body VB is introduced is defined at a position adjacent to the piston P2, and the hub-side friction plate and the drum according to the supply and discharge of the hydraulic pressure to the hydraulic chamber F2.
- the third clutch CL3 includes a rotatable inner holding member coupled to the third sun gear S3 via the power transmission members 5 and 8, a hub side friction plate engaged with the outer peripheral surface of the inner holding member, A rotatable outer holding member coupled to the ring gear R2 via the power transmission member 6, a drum side friction plate engaged with an inner peripheral surface of the outer holding member, a hub side friction plate, and a drum side friction plate. It has a piston P3 that is driven back and forth in the axial direction for pressure contact.
- a hydraulic chamber F3 into which the hydraulic pressure supplied from the valve body VB is introduced is defined at a position adjacent to the piston P3, and the hub side friction plate and the drum according to the supply and discharge of the hydraulic pressure to the hydraulic chamber F3.
- the second ring gear R2 and the third sun gear S3 are disconnected and connected by the side friction plate being pressed or released.
- the first brake BR1 connects and disconnects the transmission case 11 and the first sun gear S1 (more specifically, the front first sun gear S1a).
- the second brake BR2 connects and disconnects the transmission case 11 and the third ring gear R3.
- the first brake BR1 includes a rotatable inner holding member coupled to the front first sun gear S1a via the power transmission member 17, and a hub side friction plate engaged with the outer peripheral surface of the inner holding member.
- the drum side friction plate engaged with the inner peripheral surface of the outer holding member, the hub side friction plate and the drum side friction plate And a piston P4 that is driven back and forth in the axial direction.
- a hydraulic chamber F4 into which the hydraulic pressure supplied from the valve body VB is introduced is defined at a position adjacent to the piston P4, and the hub side friction plate and the drum according to the supply and discharge of the hydraulic pressure to the hydraulic chamber F4.
- the transmission case 11 and the first sun gear S1 are connected and disconnected by the side friction plate being pressed or released.
- the second brake BR2 includes a rotatable inner holding member coupled to the third ring gear R3, a hub side friction plate engaged with the outer peripheral surface of the inner holding member, and a non-rotatable coupled to the transmission case 11.
- a hydraulic chamber F5 into which the hydraulic pressure supplied from the valve body VB is introduced is defined at a position adjacent to the piston P5, and the hub side friction plate and the drum according to the supply and discharge of the hydraulic pressure to the hydraulic chamber F5.
- the transmission case 11 and the third ring gear R3 are connected / disconnected by the side friction plate being pressed or released.
- the transmission case 11 has an annular vertical wall portion W1 extending radially inward from the inner peripheral surface 11b of the transmission case 11 at an axial position between the first brake BR1 and the third clutch CL3, and is vertically
- a cylindrical cylindrical wall portion W2 extending rearward from the inner peripheral end of the wall portion W1 is provided.
- the cylindrical wall portion W ⁇ b> 2 is formed so as to extend concentrically along the inner peripheral surface of the power transmission member 8.
- Three housings arranged in the axial direction are formed on the radially outer side of the power transmission member 8, and the pistons P1, P1 of the first clutch CL1, the second clutch CL2, and the third clutch CL3 are formed in the three housings. P2 and P3 are accommodated, respectively.
- An oil passage is formed. Specifically, an oil passage a is formed in the vertical wall portion W1 and the cylindrical wall portion W2, and oil passages b, c, and d are formed in the power transmission member 8.
- the hydraulic pressure is supplied to the hydraulic chamber F1 of the first clutch CL1 through the oil passage a and the oil passage b, and the hydraulic pressure is supplied to the hydraulic chamber F2 of the second clutch CL2 through the oil passage a and the oil passage c. Hydraulic pressure is supplied to the hydraulic chamber F3 of the third clutch CL3 through the oil passage d.
- the communication portion between the oil passage a and the oil passages b, c, d between the outer peripheral surface of the cylindrical wall portion W2 and the inner peripheral surface of the power transmission member 8 is sealed by a seal ring.
- the piston P4 of the first brake BR1 is accommodated in a housing formed on the front side of the vertical wall portion W1.
- An oil passage e (FIG. 2) directly communicates with the hydraulic chamber F4 partitioned by the housing from the outside (valve body VB) of the transmission case 11.
- the piston P5 of the second brake BR2 is accommodated in a housing fitted to the inner peripheral surface 11b of the rear part of the transmission case 11.
- An oil passage f (FIG. 2) communicates directly with the hydraulic chamber F5 partitioned by the housing from the outside (valve body VB) of the transmission case 11.
- the first speed is formed when the first clutch CL1, the first brake BR1, and the second brake BR2 are engaged, and the second clutch CL2, the first brake BR1, and the second brake BR2 are engaged.
- Second speed is formed, and when the first clutch CL1, the second clutch CL2, and the second brake BR2 are engaged, the third speed is formed, and the second clutch CL2, the third clutch CL3, the second brake BR2 Is established, and when the first clutch CL1, the third clutch CL3, and the second brake BR2 are engaged, the fifth gear is formed, and the first clutch CL1, the second clutch CL2, and
- the third clutch CL3 is engaged, the sixth speed is formed, and when the first clutch CL1, the third clutch CL3, and the first brake BR1 are engaged.
- the eighth gear is formed, and the third clutch CL3, the first brake BR1, and the second brake BR2 are engaged.
- a reverse speed is formed when the first clutch CL1, the first brake BR1, and the second brake BR2 are engaged.
- first gear set PG1 “fourth gear set PG4”, “second gear set PG2”, and “third gear set PG3” are “first planetary gear set” in the claims.
- second gear set PG2 “second gear set PG2”
- third gear set PG3 “third gear set” in the claims.
- second gear set PG2 is “third gear set” in the claims.
- third gear set PG3 “first planetary gear set” in the claims.
- the “first sun gear S1, first carrier C1, first ring gear R1” in the first embodiment corresponds to “first sun gear, first carrier, first ring gear” in the claims.
- “fourth sun gear S4, fourth carrier C4, fourth ring gear R4” corresponds to “second sun gear, second carrier, second ring gear” in the claims
- the “second sun gear S2, second carrier C2, second ring gear R2” in the first embodiment corresponds to “third sun gear, third carrier, third ring gear” in the claims
- the “third sun gear S3, the third carrier C3, the third ring gear R3” in the first embodiment is the same as the “fourth sun gear, the fourth carrier, the fourth carrier in the claims”.
- “front first sun gear S1a” and “rear first sun gear S1b” in the first embodiment correspond to “first divided sun gear” and “second divided sun gear” in the claims, respectively.
- the automatic transmission 10 'shown in FIG. 4 is simply an application of the conventional technique described in FIG. That is, in order to use the horizontal automatic transmission as a vertical automatic transmission, the fourth gear set PG4 ′ provided on the rearmost side (the non-drive source side) is a double sun gear type, and this fourth planetary gear set A fourth carrier C4 of PG4 ′ is connected to an output shaft 13 ′ disposed on the same axis as the input shaft 12 ′.
- the automatic transmission 10 ′ shown in FIG. 4 is different from the automatic transmission 10 shown in FIGS. 1 and 2 in that the fourth gear set PG4 ′ is a double sun gear type instead of the first gear set PG1 ′.
- the first brake BR1 ′ is provided on the most rear side (reverse drive source side), and is not the first gear set PG1 ′ but the sun gear of the fourth gear set PG4 ′ (more specifically, the rear fourth sun gear S4b ′). ), And other configurations are the same.
- the fourth gear set PG4 ′ has a front fourth sun gear S4a ′ and a rear fourth sun gear S4b ′ divided in the front-rear direction, and the first brake BR1 ′ is held inside thereof.
- the member is coupled to the rear fourth sun gear S4b ′ via a power transmission member 17 ′.
- the output shaft 13 ′ passes through the inside (center portion) of the front fourth sun gear S4a ′, and via the power transmission member 18 ′ passing between the pair of fourth sun gears S4a ′ and S4b ′, the fourth carrier C4. Is bound to.
- the output shaft 13 ′ passes through the inside of the rear fourth sun gear S4b ′ of the fourth gear set PG4 ′.
- the diameter needs to be larger than that of the input shaft 12 '. For this reason, the diameter of the rear fourth sun gear S4b ' also increases, and accordingly, the overall diameter of the fourth gear set PG4' increases.
- the inner side of the front first sun gear S1a in the first gear set PG1 ( Since the input shaft 12 passes through the center portion and the output shaft 13 is always connected to the fourth carrier C4 of the fourth gear set PG4, the output shaft 13 whose diameter is increased to transmit a large torque is the split sun gear. An increase in the diameter of the planetary gear set due to passing through the center is avoided. Therefore, as shown in FIGS. 1 and 2, the diameter of the transmission case 11 surrounding the fourth gear set PG4 can be reduced to form the reduced diameter portion 11x, and the configuration of the comparative example of FIG. 4 is adopted. Compared with the case (the transmission case in this case is indicated by a two-dot chain line L in FIG. 2), the radial dimension of the end portion on the output side of the automatic transmission 10 can be reduced. It is possible to improve the comfort of seats.
- the input shaft 12 passes through the inside of the split sun gear S1a.
- the input shaft 12 has a smaller transmission torque than the output shaft 13 and can have a small diameter.
- An increase in the diameter of the gear set PG1 is small, and an increase in the diameter on the input side of the automatic transmission 10 can be suppressed.
- 5 and 6 are a cross-sectional view and a skeleton diagram showing the configuration of the automatic transmission 20 according to the second embodiment of the present invention.
- the same reference numerals as those used in the first embodiment are used for the configuration relating to the gear set and the frictional engagement elements. The same applies to third to fifth embodiments described later.
- the automatic transmission 20 of the second embodiment is a vertical automatic transmission as in the first embodiment, and is inserted into the transmission case 21 from the transmission case 21 and the vehicle front side (drive source).
- the input shaft 22 and the output shaft 23 projecting from the inside of the transmission case 21 to the vehicle rear side (reverse drive source side).
- the input shaft 22 and the output shaft 23 are disposed on the same axial center, and the first, second, third, and fourth gear sets PG1, PG2, PG3, and PG4 are sequentially disposed on the axial center from the front side. Yes.
- a first clutch CL1 is disposed on the front side of the first gear set PG1 in the transmission case 21, a second clutch CL2 is disposed on the rear side of the first gear set PG1, and the second clutch CL2 and the second gear set PG2 are disposed.
- the third clutch CL3 is disposed between the two.
- a first brake BR1 is disposed on the front side of the first clutch CL3, and a second brake BR2 is disposed on the radially outer side of the third gear set PG3.
- the frictional engagement elements (the first to third clutches CL1 to CL3 and the first and second brakes BR1 and BR2) of the automatic transmission 10 are connected to the first brake BR1 and the first brake from the front side (drive source side).
- the clutch CL1, the second clutch CL2, the third clutch CL3, and the second brake BR2 are arranged in the axial direction in this order.
- the first to fourth gear sets PG1 to PG4 are single pinion type planetary gear sets similar to those in the first embodiment.
- the first gear set PG1 has a first sun gear S1, a first ring gear R1, and a first carrier C1
- the second gear set PG2 has a second sun gear S2, a second ring gear R2, and a second carrier C2.
- the third gear set PG3 has a third sun gear S3, a third ring gear R3, and a third carrier C3
- the fourth gear set PG4 has a fourth sun gear S4, a fourth ring gear R4, and a fourth carrier C4.
- the first gear set PG1 is a double sun gear type similar to that in the first embodiment. That is, the first sun gear S1 has a front first sun gear S1a and a rear first sun gear S1b that are divided in the axial direction.
- the first sun gear S1 (more specifically, the rear first sun gear S1b) and the fourth sun gear S4 are always connected, the first ring gear R1 and the second sun gear S2 are always connected, The second carrier C2 and the fourth carrier C4 are always connected, and the third carrier C3 and the fourth ring gear R4 are always connected.
- the input shaft 22 is always connected to the first carrier C1, and the output shaft 13 is always connected to the fourth carrier C4.
- the input shaft 12 is coupled to the first carrier C1 via a power transmission member 28 that passes between the pair of front and rear first sun gears S1a and S1b.
- the rear first sun gear S1b and the fourth sun gear S4 are connected to each other via a power transmission member 25.
- the fourth carrier C4 and the second carrier C2 are connected to each other via the power transmission member 26.
- the first clutch CL1 connects and disconnects the input shaft 22, the first carrier C1, and the third sun gear S3.
- the second clutch CL2 connects and disconnects the first ring gear R1, the second sun gear S2, and the third sun gear S3.
- the third clutch CL3 connects and disconnects the second ring gear R2 and the third sun gear S3.
- the first clutch CL1 transmits power to the rotatable inner holding member coupled to the first carrier C1, the hub-side friction plate engaged with the outer peripheral surface of the inner holding member, and the third sun gear S3.
- a rotatable outer holding member coupled via members 31, 32, 33, and 34; a drum side friction plate engaged with an inner peripheral surface of the outer holding member; a hub side friction plate and a drum side friction plate; And a piston P1 that is driven back and forth in the axial direction.
- a hydraulic chamber F1 into which the hydraulic pressure supplied from the valve body VB (FIG. 5) is introduced is defined at a position adjacent to the piston P1, and the hub side according to the supply and discharge of hydraulic pressure to the hydraulic chamber F1 is defined.
- the input shaft 22, the first carrier C1, and the third sun gear S3 are disconnected and connected by the friction plate and the drum side friction plate being pressed or released.
- the second clutch CL2 includes a rotatable inner holding member coupled to the first ring gear R1 and the second sun gear S2 via the power transmission member 35, and a hub side friction plate engaged with the outer peripheral surface of the inner holding member.
- a rotatable outer holding member coupled to the third sun gear S3 via power transmission members 32, 33, 34, a drum side friction plate engaged with an inner peripheral surface of the outer holding member, and a hub side friction plate
- a piston P2 that is driven back and forth in the axial direction to press-contact the drum side friction plate.
- a hydraulic chamber F2 into which the hydraulic pressure supplied from the valve body VB is introduced is defined at a position adjacent to the piston P2, and the hub-side friction plate and the drum according to the supply and discharge of the hydraulic pressure to the hydraulic chamber F2.
- the third clutch CL3 includes a rotatable inner holding member coupled to the second ring gear R2, a hub-side friction plate engaged with the outer peripheral surface of the inner holding member, and a power transmission member 34 to the third sun gear S3.
- a rotatable outer holding member coupled to each other, a drum-side friction plate engaged with the inner peripheral surface of the outer holding member, and an axially driven forward / backward drive to press-contact the hub-side friction plate and the drum-side friction plate And a piston P3.
- a hydraulic chamber F3 into which the hydraulic pressure supplied from the valve body VB is introduced is defined at a position adjacent to the piston P3, and the hub side friction plate and the drum according to the supply and discharge of the hydraulic pressure to the hydraulic chamber F3.
- the second ring gear R2 and the third sun gear S3 are disconnected and connected by the side friction plate being pressed or released.
- the first brake BR1 connects and disconnects the transmission case 21 and the first sun gear S1 (more specifically, the front first sun gear S1a).
- the second brake BR2 connects and disconnects the transmission case 21 and the third ring gear R3.
- the first brake BR1 includes a rotatable inner holding member coupled to the front first sun gear S1a via a power transmission member 37, and a hub side friction plate engaged with the outer peripheral surface of the inner holding member.
- the drum side friction plate engaged with the inner peripheral surface of the outer holding member, the hub side friction plate and the drum side friction plate And a piston P4 that is driven back and forth in the axial direction.
- a hydraulic chamber F4 into which the hydraulic pressure supplied from the valve body VB is introduced is defined at a position adjacent to the piston P4, and the hub side friction plate and the drum according to the supply and discharge of the hydraulic pressure to the hydraulic chamber F4.
- the transmission case 21 and the first sun gear S1 are connected or disconnected by the side friction plate being pressed or released.
- the second brake BR2 includes a non-rotatable inner holding member coupled to the transmission case 21, a hub-side friction plate engaged with the outer peripheral surface of the inner holding member, and a rotatable coupled to the third ring gear R3.
- a hydraulic chamber F5 into which the hydraulic pressure supplied from the valve body VB is introduced is defined at a position adjacent to the piston P5, and the hub side friction plate and the drum according to the supply and discharge of the hydraulic pressure to the hydraulic chamber F5.
- the transmission case 21 and the third ring gear R3 are connected / disconnected by pressing or releasing the side friction plate.
- the transmission case 21 has a front vertical wall portion W3 having a T-shaped cross section extending radially inward from the inner peripheral surface 21b of the transmission case 21 at an axial position between the first brake BR1 and the first clutch CL1. Have.
- the inner peripheral end of the front vertical wall W3 is formed to extend in the front-rear direction along the outer peripheral surface of the power transmission member 31.
- the transmission case 21 is an intermediate vertical wall portion having a T-shaped cross section extending radially inward from the inner peripheral surface 21b of the transmission case 21 at an axial position between the second clutch CL2 and the third clutch CL3. W4.
- the inner peripheral end of the intermediate vertical wall W4 is formed to extend in the front-rear direction along the power transmission member 33 at a position surrounded by the power transmission member 33 from inside and outside in the radial direction.
- the piston P1 of the first clutch CL1 is housed in a housing formed integrally with the power transmission members 31 and 32.
- the front vertical wall W3 and the power transmission member 31 are formed with an oil passage for supplying hydraulic pressure to the hydraulic chamber F1 defined by the housing.
- an oil passage g is formed in the front vertical wall portion W3, and an oil passage h is formed in the power transmission member 31. Then, the hydraulic pressure is supplied to the hydraulic chamber F1 of the first clutch CL1 through the oil passage g and the oil passage h.
- the piston P2 of the second clutch CL2 is housed in a housing formed integrally with the power transmission members 32 and 33.
- the piston P3 of the third clutch CL3 is accommodated in a housing formed integrally with the power transmission members 33 and 34.
- the intermediate vertical wall W4 and the power transmission member 33 are formed with oil passages for supplying hydraulic pressure to the hydraulic chambers F2, F3 partitioned by these housings. Specifically, an oil passage i is formed in the intermediate vertical wall portion W4, and oil passages j and k are formed in the power transmission member 33.
- the hydraulic pressure is supplied to the hydraulic chamber F2 of the second clutch CL2 through the oil passage i and the oil passage j, and the hydraulic pressure is supplied to the hydraulic chamber F3 of the third clutch CL3 through the oil passage i and the oil passage k.
- the piston P4 of the first brake BR1 is housed in a housing formed on the front side of the front vertical wall W3.
- An oil passage e (FIG. 6) directly communicates with the hydraulic chamber F4 partitioned by the housing from the outside (valve body VB) of the transmission case 21.
- the piston P5 of the second brake BR2 is housed in a housing inserted and fixed from the rear inside the rear end of the transmission case 21.
- An oil passage f directly communicates with the hydraulic chamber F5 partitioned by the housing from the outside (valve body VB) of the transmission case 21.
- the hydraulic supply / discharge control for the hydraulic chambers F1 to F5 is performed. Based on the selective engagement of three specific frictional engagement elements among the five frictional engagement elements (CL1, CL2, CL3, BR1, BR2) Is formed.
- the automatic transmission 20 like the automatic transmission 10 according to the first embodiment, the inner side of the front first sun gear S1a of the first gear set PG1 of the double sun gear type ( Since the input shaft 22 passes through the central portion) and the output shaft 23 is always connected to the fourth gear set PG4, the output shaft 23 whose diameter is increased to transmit a large torque passes through the inside of the split sun gear. An increase in the diameter of the planetary gear set is avoided. Therefore, the radial dimension of the output side (rear side) end of the automatic transmission 20 can be reduced, and the comfortability of the driver seat and the passenger seat can be improved.
- the fourth gear set is different from the case of the first embodiment.
- the diameter of the transmission case 21 surrounding the PG 4 cannot be reduced.
- the fourth gear set PG4 is a double sun gear type, the diameter of the rear part of the transmission case 21 is further enlarged (the transmission case in that case is indicated by a two-dot chain line L in FIG. 6). Compared to the case, the automatic transmission can be made more compact.
- FIG. 7 is a skeleton diagram showing a configuration of an automatic transmission 40 according to the third embodiment of the present invention.
- This automatic transmission 40 is a vertical installation type automatic transmission as in the first embodiment, and includes a transmission case 41 and an input shaft 42 inserted into the transmission case 41 from the vehicle front side (drive source). And an output shaft 43 projecting from the inside of the transmission case 41 to the vehicle rear side (counter drive source side).
- the input shaft 42 and the output shaft 43 are disposed on the same axial center, and the first, second, third, and fourth gear sets PG1, PG2, PG3, and PG4 are sequentially disposed on the axial center from the front side. Yes.
- a first clutch CL1 is disposed on the front side of the first gear set PG1 in the transmission case 41, a second clutch CL2 is disposed on the radially outer side of the first clutch CL1 and the first gear set PG1, A third clutch CL3 is disposed outside the gear set PG2 in the radial direction.
- a first brake BR1 is disposed on the front side of the first clutch CL1 and the second clutch CL2, and a second brake BR2 is disposed on the outer side in the radial direction of the third gear set PG3.
- the frictional engagement elements (the first to third clutches CL1 to CL3 and the first and second brakes BR1 and BR2) of the automatic transmission 40 are connected to the first brake BR1 and the first brake from the front side (drive source side).
- the clutch CL1 (or the second clutch CL2), the third clutch CL3, and the second brake BR2 are arranged in the axial direction in this order.
- the first to fourth gear sets PG1 to PG4 are single pinion type planetary gear sets similar to those in the first embodiment.
- the first gear set PG1 has a first sun gear S1, a first ring gear R1, and a first carrier C1
- the second gear set PG2 has a second sun gear S2, a second ring gear R2, and a second carrier C2.
- the third gear set PG3 has a third sun gear S3, a third ring gear R3, and a third carrier C3
- the fourth gear set PG4 has a fourth sun gear S4, a fourth ring gear R4, and a fourth carrier C4.
- the first gear set PG1 is a double sun gear type similar to that in the first embodiment. That is, the first sun gear S1 has a front first sun gear S1a and a rear first sun gear S1b that are divided in the axial direction.
- the first sun gear S1 (more specifically, the rear first sun gear S1b) and the fourth sun gear S4 are always connected, the first ring gear R1 and the second sun gear S2 are always connected, The second carrier C2 and the fourth carrier C4 are always connected, and the third carrier C3 and the fourth ring gear R4 are always connected.
- the input shaft 42 is always connected to the first carrier C1, and the output shaft 13 is always connected to the fourth carrier C4.
- the input shaft 42 is coupled to the first carrier C1 via a power transmission member 48 that passes between the pair of front and rear first sun gears S1a and S1b.
- the rear first sun gear S1b and the fourth sun gear S4 are connected to each other via a power transmission member 45.
- the fourth carrier C4 and the second carrier C2 are coupled via a power transmission member 46.
- the first clutch CL1 connects and disconnects the input shaft 42, the first carrier C1, and the third sun gear S3.
- the second clutch CL2 connects and disconnects the first ring gear R1, the second sun gear S2, and the third sun gear S3.
- the third clutch CL3 connects and disconnects the second ring gear R2 and the third sun gear S3.
- the first clutch CL1 includes a rotatable inner holding member coupled to the third sun gear S3 via power transmission members 51, 52, and 53, and a hub side engaged with the outer peripheral surface of the inner holding member.
- the friction plate, the rotatable outer holding member coupled to the first carrier C1, the drum side friction plate engaged with the inner peripheral surface of the outer holding member, the hub side friction plate and the drum side friction plate are pressed against each other.
- it has a piston P1 that is driven back and forth in the axial direction.
- a hydraulic chamber F1 into which hydraulic pressure supplied from a valve body (not shown) is introduced is defined at a position adjacent to the piston P1, and the hub side friction plate is adapted to supply and discharge hydraulic pressure to the hydraulic chamber F1.
- the second clutch CL2 includes a rotatable inner holding member coupled to the first ring gear R1 and the second sun gear S2 via the power transmission member 55, and a hub side friction plate engaged with the outer peripheral surface of the inner holding member.
- a rotatable outer holding member coupled to the third sun gear S3 via power transmission members 52, 53, a drum side friction plate engaged with an inner peripheral surface of the outer holding member, a hub side friction plate and a drum It has a piston P2 that is driven back and forth in the axial direction to press-contact the side friction plate.
- a hydraulic chamber F2 into which the hydraulic pressure supplied from the valve body is introduced is defined at a position adjacent to the piston P2, and the hub-side friction plate and the drum according to the supply and discharge of the hydraulic pressure to the hydraulic chamber F2.
- the side friction plate is pressed or released, the first ring gear R1, the second sun gear S2, and the third sun gear S3 are disconnected.
- the third clutch CL3 includes a rotatable inner holding member coupled to the second ring gear R2, a hub side friction plate engaged with the outer peripheral surface of the inner holding member, and a third sun gear S3 via a power transmission member 53.
- a rotatable outer holding member coupled to each other, a drum-side friction plate engaged with the inner peripheral surface of the outer holding member, and an axially driven forward / backward drive to press-contact the hub-side friction plate and the drum-side friction plate And a piston P3.
- a hydraulic chamber F3 into which hydraulic pressure supplied from the valve body is introduced is defined at a position adjacent to the piston P3, and the hub-side friction plate and the drum according to the supply and discharge of hydraulic pressure to the hydraulic chamber F3.
- the second ring gear R2 and the third sun gear S3 are disconnected and connected by the side friction plate being pressed or released.
- the counterparts to which the inner holding members of the first to third clutches CL1 to CL3 are coupled are all gear sets (first gear set PG1) located radially inward of the clutches CL1 to CL3.
- the rotating element of the second gear set PG2), a power transmission member 45 for connecting the rear first sun gear S1b and the fourth sun gear S4, and a power transmission member 46 for connecting the second carrier C2 and the fourth carrier C4. are arranged so as to pass through the inside of the power transmission member 53 that connects the third sun gear S3 and the power transmission member 52.
- the third embodiment there is no need to provide another power transmission member or the like between the power transmission member 52 and the inner peripheral surface 41b of the transmission case 41, and the power transmission member 52 is used as the transmission.
- the case 41 may be disposed so as to directly face the inner peripheral surface 41 b of the case 41. That is, in the third embodiment, there are no parts (for example, a planetary gear set or other power transmission members) surrounding the first to third clutches CL1 to CL3 other than the power transmission member 52. Therefore, the first to third clutches CL1 to CL3 can be easily housed in the transmission case 41.
- the first brake BR1 connects and disconnects the transmission case 41 and the first sun gear S1 (more specifically, the front first sun gear S1a).
- the second brake BR2 connects and disconnects the transmission case 41 and the third ring gear R3.
- the first brake BR1 includes a rotatable inner holding member coupled to the front first sun gear S1a via a power transmission member 47, and a hub side friction plate engaged with the outer peripheral surface of the inner holding member.
- the drum side friction plate engaged with the inner peripheral surface of the outer holding member, the hub side friction plate and the drum side friction plate And a piston P4 that is driven back and forth in the axial direction.
- a hydraulic chamber F4 into which hydraulic pressure supplied from the valve body is introduced is defined at a position adjacent to the piston P4, and the hub-side friction plate and the drum according to the supply and discharge of hydraulic pressure to the hydraulic chamber F4.
- the transmission case 41 and the first sun gear S1 are connected or disconnected by the side friction plate being pressed or released.
- the second brake BR2 includes a rotatable inner holding member coupled to the third ring gear R3, a hub side friction plate engaged with an outer peripheral surface of the inner holding member, and a non-rotatable coupled to the transmission case 41.
- a hydraulic chamber F5 into which hydraulic pressure supplied from the valve body is introduced is defined at a position adjacent to the piston P5, and the hub-side friction plate and the drum according to the supply and discharge of hydraulic pressure to the hydraulic chamber F5.
- the transmission case 41 and the third ring gear R3 are connected / disconnected by pressing or releasing the side friction plate.
- the transmission case 41 is an annular front vertical wall portion extending radially inward from the inner peripheral surface 41b of the transmission case 41 at an axial position between the first brake BR1 and the first and second clutches CL1 and CL2. It has W5 and has a cylindrical front cylindrical wall W6 that extends rearward from the inner peripheral end of the front vertical wall W5.
- the transmission case 41 has an annular intermediate vertical wall portion W7 extending radially inward from the inner peripheral surface 41b of the transmission case 41 at an axial position between the third clutch CL3 and the second brake BR2.
- a cylindrical intermediate cylindrical wall portion W8 extending forward from the inner peripheral end of the intermediate vertical wall portion W7 is provided.
- the piston P1 of the first clutch CL1 is accommodated in a housing formed so as to extend rearward from the front vertical wall portion W5 on the radially outer side of the front cylindrical wall portion W6.
- An oil passage m for supplying hydraulic pressure to the hydraulic chamber F1 defined by the housing is formed in the front vertical wall portion W5 and the front cylindrical wall portion W6.
- the piston P2 of the second clutch CL2 is accommodated in a housing formed so as to extend rearward from the front vertical wall W5 on the radially outer side of the first clutch CL1.
- the power transmission member 51 is formed with an oil passage n communicating with the hydraulic chamber F2 defined by the housing. That is, hydraulic pressure is supplied to the hydraulic chamber F2 through the oil passage m formed in the front vertical wall portion W5 and the front cylindrical wall portion W6 and the oil passage n formed in the power transmission member 51.
- the housing of the first clutch CL1 and the housing of the second clutch CL2 are integrally formed with an internal / external double positional relationship.
- the piston P3 of the third clutch CL3 is accommodated in a housing formed so as to extend forward from the intermediate vertical wall portion W7 on the radially outer side of the intermediate cylindrical wall portion W8.
- An oil passage p for supplying hydraulic pressure to the hydraulic chamber F3 defined by the housing is formed in the intermediate vertical wall portion W7 and the intermediate cylindrical wall portion W8.
- the piston P4 of the first brake BR1 is accommodated in a housing formed to extend forward from the front vertical wall W5.
- An oil passage e directly communicates with the hydraulic chamber F4 partitioned by the housing from the outside of the transmission case 41.
- the piston P5 of the second brake BR2 is housed in a housing formed to extend rearward from the intermediate vertical wall W7.
- An oil passage f communicates directly from the outside of the transmission case 41 to the hydraulic chamber F5 partitioned by the housing.
- the communicating portions of the oil passages m, n, and p between the outer peripheral surfaces of the cylindrical wall portions W6 and W8 and the inner peripheral surfaces of the housings of the first and third clutches CL1 and CL3 are respectively seal rings. It is sealed by.
- the hydraulic pressure supply / discharge control for the hydraulic chambers F1 to F5 is performed. Based on the selective engagement of three specific frictional engagement elements among the five frictional engagement elements (CL1, CL2, CL3, BR1, BR2) Is formed.
- the inner side of the front first sun gear S1a of the first gear set PG1 of the double sun gear type ( Since the input shaft 42 passes through the center portion and the output shaft 43 is always connected to the fourth gear set PG4, the output shaft 43 having a large diameter to transmit a large torque passes through the inside of the split sun gear. An increase in the diameter of the planetary gear set is avoided. Therefore, the diameter of the transmission case 41 surrounding the fourth gear set PG4 can be reduced to form the reduced diameter portion 41x. If the fourth gear set PG4 is a double sun gear type (the transmission case in that case) 7 is indicated by a two-dot chain line L in FIG. 7, the radial dimension of the end portion on the output side (rear side) of the automatic transmission 40 can be reduced.
- an automatic transmission 60 (FIG. 8) according to the fourth embodiment includes an input shaft 62 and an output shaft 63 disposed on the same axis, and an input shaft 62 and an output shaft 63.
- the first, second, third, and fourth gear sets PG1, PG2, PG3, and PG4 are sequentially arranged on the shaft center from the front side (drive source side).
- the automatic transmission 70 (FIG.
- the fifth embodiment includes an input shaft 72 and an output shaft 73 disposed on the same axis, and a front side (on the axis of the input shaft 72 and the output shaft 73) (
- the first, second, third, and fourth gear sets PG1, PG2, PG3, and PG4 are arranged in order from the drive source side).
- a fourth clutch CL4 is additionally provided as a frictional engagement element with respect to the automatic transmission 10 of the first embodiment.
- the fourth clutch CL4 is arranged in the vicinity of the rear side of the fourth gear set PG4 in the transmission case (61 or 71), that is, the most counter drive source side in the axial direction.
- the connection relationship between the rotating elements, the rotation elements between the frictional engagement elements, or the transmission is the same as that of the automatic transmission 10 according to the third embodiment.
- the fourth clutch CL4 connects and disconnects the fourth ring gear R4, the fourth carrier C4, and the output shaft 63. That is, the fourth clutch CL4 is rotatable coupled to the rotatable inner holding member coupled to the output shaft 63, the hub side friction plate engaged with the outer peripheral surface of the inner retaining member, and the fourth ring gear R4. An outer holding member, a drum-side friction plate engaged with the inner peripheral surface of the outer holding member, and a piston P6 driven forward and backward in the axial direction to press-contact the hub-side friction plate and the drum-side friction plate. Have.
- the transmission case 61 includes an annular rear vertical wall portion W9 extending radially inward from the inner peripheral surface 61b of the rear end portion, and a rear vertical wall portion W9. And a cylindrical rear cylindrical wall portion W10 extending forward from the inner peripheral end.
- the piston P6 is accommodated in a housing formed to extend rearward from the rear vertical wall portion W9 on the radially outer side of the rear cylindrical wall portion W10.
- An oil path q for supplying hydraulic pressure to the hydraulic chamber F6 defined by the housing is formed in the rear vertical wall portion W9 and the rear cylindrical wall portion W10.
- the fourth clutch CL4 connects and disconnects the fourth sun gear S4, the fourth carrier C4, and the output shaft 73. That is, the fourth clutch CL4 is engaged with the rotatable inner holding member coupled to the power transmission member 75 that connects the rear first sun gear S1b and the fourth sun gear S4, and the outer peripheral surface of the inner holding member.
- the transmission case 71 includes an annular rear vertical wall portion W11 extending radially inward from the inner peripheral surface 71b of the rear end portion, and a rear vertical wall portion W11. And a cylindrical rear cylindrical wall portion W12 extending forward from the inner peripheral end.
- the piston P6 is accommodated in a housing formed to extend rearward from the rear vertical wall portion W11 on the radially outer side of the rear cylindrical wall portion W12.
- An oil passage r for supplying hydraulic pressure to the hydraulic chamber F6 partitioned by the housing is formed in the rear vertical wall portion W11 and the rear cylindrical wall portion W12.
- One of the first to ninth forward speeds and one of the reverse speeds can be selected by selectively engaging three specific frictional engagement elements among the six frictional engagement elements (CL1, CL2, CL3, CL4, BR1, BR2). Is formed.
- the first speed is formed when the first clutch CL1, the first brake BR1, and the second brake BR2 are engaged, and the second clutch CL2, the first brake BR1, and the second brake BR2 are engaged.
- Second speed is formed, and when the second clutch CL2, the fourth clutch CL4, and the second brake BR2 are engaged, the third speed is formed, and the first clutch CL1, the second clutch CL2, and the second brake
- the fourth speed is formed, and when the second clutch CL2, the third clutch CL3, and the second brake BR2 are engaged, the fifth speed is formed, and the first clutch CL1, the third clutch CL3,
- the sixth speed is formed, and the first clutch CL1, the second clutch CL2, and the third clutch CL3 are engaged.
- the front first sun gear of the first gear set PG1 of the double sun gear type is used. Since the input shafts 62 and 72 pass through the inside (center portion) of S1a and the output shafts 63 and 73 are always connected to the fourth gear set PG4, the output shaft 63 whose diameter is increased to transmit a large torque, An increase in the diameter of the planetary gear set due to 73 passing inside the split sun gear is avoided. Accordingly, the diameter of the transmission case 41 surrounding the fourth gear set PG4 can be reduced to form the reduced diameter portions 61x and 71x.
- the fourth gear set PG4 is a double sun gear type (in this case, the speed change) Compared with the machine case (indicated by a two-dot chain line L in FIGS. 8 and 9), the radial dimension of the end portion on the output side of the automatic transmissions 60 and 70 can be reduced.
- the automatic transmission includes an input shaft connected to a drive source, an output shaft disposed on the same axis as the input shaft on the opposite drive source side of the input shaft, a first sun gear, A first planetary gear set having a first carrier and a first ring gear; and a second sun gear, a second carrier, and a second ring gear, which are disposed on the side opposite to the driving source of the first planetary gear set.
- the first sun gear has a first split sun gear on the drive source side and a second split sun gear on the counter drive source side, and the first split sun gear is connected to the first brake and the first split sun gear.
- the second split sun gear is always connected to the second sun gear, and the input shaft is connected to the inside of the first split sun gear and the first and second split gears.
- the first shaft is always connected to the first carrier through the sun gear, and the output shaft is always connected to the second carrier.
- the diameter is large in order to transmit a large torque.
- the increase in the diameter of the planetary gear set due to the output shaft passing through the inside of the split sun gear is avoided, the increase in the radial dimension of the output side end of the automatic transmission, and the driver's seat in the FR vehicle resulting from this In addition, the deterioration of the comfortability of the passenger seat is suppressed.
- the input shaft passes through the inside of the split sun gear.
- the input shaft has a smaller transmission torque than the output shaft and can have a small diameter, there is little increase in the diameter of the first planetary gear set. An increase in the diameter on the input side of the automatic transmission is also suppressed.
- the automatic transmission preferably includes a third planetary gear set having a third sun gear, a third carrier, and a third ring gear, and a fourth sun gear, a fourth carrier, and a fourth ring gear. It further has a fourth planetary gear set, a first clutch, a second clutch, a third clutch, and a second brake.
- the first ring gear and the third sun gear are always connected, the second carrier and the third carrier are always connected, and the second ring gear and the fourth carrier are always connected.
- the first clutch connects and disconnects the fourth sun gear, the input shaft, and the first carrier, and the second clutch includes the fourth sun gear, the first ring gear, and the third gear.
- the third clutch connects and disconnects the fourth sun gear and the third ring gear, and the second brake disconnects the fourth ring gear and the transmission case. Touch.
- the automatic transmission capable of obtaining the above-described effect can be realized more specifically.
- the first speed is formed when the first clutch, the first brake, and the second brake are engaged, and the second clutch, the first brake, and the second brake are formed.
- 2 is formed when the first clutch, the second clutch, and the second brake are engaged
- the third speed is formed
- the second clutch, the third clutch, and Fourth speed is formed when the second brake is engaged
- fifth speed is formed when the first clutch, the third clutch, and the second brake are engaged
- the first clutch, 6-speed is formed when the second clutch and the third clutch are engaged
- 7-speed is formed when the first clutch, the third clutch, and the first brake are engaged
- the eighth speed is formed when the second clutch, the third clutch, and the first brake are engaged, and the reverse speed is established when the third clutch, the first brake, and the second brake are engaged. Is formed.
- the automatic transmission connects / disconnects the second sun gear, the second carrier, and the output shaft, or connects / disconnects the second ring gear, the second carrier, and the output shaft.
- a fourth clutch may be further included.
- the first speed is formed when the first clutch, the first brake, and the second brake are engaged, and the second clutch
- the first clutch The second speed is formed when the brake and the second brake are engaged
- the third speed is formed when the second clutch, the fourth clutch, and the second brake are engaged
- the first clutch 4th speed is formed when the second clutch and the second brake are engaged
- 5th speed is formed when the second clutch, the third clutch and the second brake are engaged
- Sixth speed is formed when the first clutch, the third clutch, and the second brake are engaged, and the first clutch, the second clutch, and the third clutch are engaged.
- 7th speed is sometimes formed, and 8th speed is formed when the first clutch, the third clutch, and the first brake are engaged, and the second clutch, the third clutch, and the first brake are formed.
- 9 is formed when the second clutch is engaged, and a reverse speed is formed when the third clutch, the first brake, and the second brake are engaged.
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Abstract
Description
Claims (5)
- 駆動源に連結された入力軸と、
該入力軸の反駆動源側において該入力軸と同一軸心上に配置された出力軸と、
第1のサンギヤ、第1のキャリヤ、及び第1のリングギヤを有する第1のプラネタリギヤセットと、
該第1のプラネタリギヤセットの反駆動源側に配置され、第2のサンギヤ、第2のキャリヤ、及び第2のリングギヤを有する第2のプラネタリギヤセットと、
前記第1のプラネタリギヤセットの駆動源側に配置された第1ブレーキと、
前記第1、第2のプラネタリギヤセットと第1ブレーキとを内部に収容する変速機ケースとを備え、
前記第1のサンギヤは、駆動源側の第1分割サンギヤと反駆動源側の第2分割サンギヤとを有し、
前記第1分割サンギヤは、前記第1ブレーキに連結されるとともに、該第1ブレーキの締結時に前記変速機ケースに固定され、
前記第2分割サンギヤは、前記第2のサンギヤに常時連結され、
前記入力軸は、前記第1分割サンギヤの内側と、前記第1、第2分割サンギヤの間とを通って前記第1のキャリヤに常時連結され、
前記出力軸は、前記第2のキャリヤに常時連結されている
ことを特徴とする自動変速機。 - 第3のサンギヤ、第3のキャリヤ、及び第3のリングギヤを有する第3のプラネタリギヤセットと、
第4のサンギヤ、第4のキャリヤ、及び第4のリングギヤを有する第4のプラネタリギヤセットと、
第1クラッチ、第2クラッチ、及び第3クラッチと、
第2ブレーキとをさらに有し、
前記第1のリングギヤと前記第3のサンギヤとが常時連結され、
前記第2のキャリヤと前記第3のキャリヤとが常時連結され、
前記第2のリングギヤと前記第4のキャリヤとが常時連結され、
前記第1クラッチは、前記第4のサンギヤと、前記入力軸及び前記第1のキャリヤとを断接し、
前記第2クラッチは、前記第4のサンギヤと、前記第1のリングギヤ及び前記第3のサンギヤとを断接し、
前記第3クラッチは、前記第4のサンギヤと、前記第3のリングギヤとを断接し、
前記第2ブレーキは、前記第4のリングギヤと、前記変速機ケースとを断接する
ことを特徴とする請求項1に記載の自動変速機。 - 前記第1クラッチ、前記第1ブレーキ、及び前記第2ブレーキが締結されたときに1速が形成され、
前記第2クラッチ、前記第1ブレーキ、及び前記第2ブレーキが締結されたときに2速が形成され、
前記第1クラッチ、前記第2クラッチ、及び前記第2ブレーキが締結されたときに3速が形成され、
前記第2クラッチ、前記第3クラッチ、及び前記第2ブレーキが締結されたときに4速が形成され、
前記第1クラッチ、前記第3クラッチ、及び前記第2ブレーキが締結されたときに5速が形成され、
前記第1クラッチ、前記第2クラッチ、及び前記第3クラッチが締結されたときに6速が形成され、
前記第1クラッチ、前記第3クラッチ、及び前記第1ブレーキが締結されたときに7速が形成され、
前記第2クラッチ、前記第3クラッチ、及び前記第1ブレーキが締結されたときに8速が形成され、
前記第3クラッチ、前記第1ブレーキ、及び前記第2ブレーキが締結されたときに後退速が形成される
ことを特徴とする請求項2に記載の自動変速機。 - 前記第2のサンギヤと、前記第2のキャリヤ及び前記出力軸とを断接するか、または、前記第2のリングギヤと、前記第2のキャリヤ及び前記出力軸とを断接する第4クラッチをさらに有する
ことを特徴とする請求項2に記載の自動変速機。 - 前記第1クラッチ、前記第1ブレーキ、及び前記第2ブレーキが締結されたときに1速が形成され、
前記第2クラッチ、前記第1ブレーキ、及び前記第2ブレーキが締結されたときに2速が形成され、
前記第2クラッチ、前記第4クラッチ、及び前記第2ブレーキが締結されたときに3速が形成され、
前記第1クラッチ、前記第2クラッチ、及び前記第2ブレーキが締結されたときに4速が形成され、
前記第2クラッチ、前記第3クラッチ、及び前記第2ブレーキが締結されたときに5速が形成され、
前記第1クラッチ、前記第3クラッチ、及び前記第2ブレーキが締結されたときに6速が形成され、
前記第1クラッチ、前記第2クラッチ、及び前記第3クラッチが締結されたときに7速が形成され、
前記第1クラッチ、前記第3クラッチ、及び前記第1ブレーキが締結されたときに8速が形成され、
前記第2クラッチ、前記第3クラッチ、及び前記第1ブレーキが締結されたときに9速が形成され、
前記第3クラッチ、前記第1ブレーキ、及び前記第2ブレーキが締結されたときに後退速が形成される
ことを特徴とする請求項4に記載の自動変速機。
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CN201580049683.2A CN107076273B (zh) | 2014-10-23 | 2015-10-20 | 自动变速器 |
DE112015004801.4T DE112015004801B4 (de) | 2014-10-23 | 2015-10-20 | Automatisch schaltbares Getriebe |
JP2016555223A JP6210168B2 (ja) | 2014-10-23 | 2015-10-20 | 自動変速機 |
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CN107076273B (zh) | 2019-08-13 |
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US9989127B2 (en) | 2018-06-05 |
US20170284516A1 (en) | 2017-10-05 |
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DE112015004801B4 (de) | 2020-08-06 |
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