WO2006049034A1 - 無段変速機の前後進切替装置 - Google Patents
無段変速機の前後進切替装置 Download PDFInfo
- Publication number
- WO2006049034A1 WO2006049034A1 PCT/JP2005/019545 JP2005019545W WO2006049034A1 WO 2006049034 A1 WO2006049034 A1 WO 2006049034A1 JP 2005019545 W JP2005019545 W JP 2005019545W WO 2006049034 A1 WO2006049034 A1 WO 2006049034A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- carrier
- switching device
- continuously variable
- variable transmission
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
- F16H3/60—Gearings for reversal only
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
- F16H37/022—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing the toothed gearing having orbital motion
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/027—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with a gear using endless flexible members for reversing rotary motion only
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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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/3023—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure
- F16H63/3026—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure comprising friction clutches or brakes
Definitions
- the present invention relates to a forward / reverse switching device for a continuously variable transmission, and more particularly to a forward / reverse switching device including a planetary gear mechanism, a reverse brake, and a direct clutch.
- Patent Document 1 discloses a continuously variable transmission having a forward / reverse switching device, a belt-type continuously variable transmission, and a differential device, wherein the forward / reverse switching device has one single pinion type.
- the planetary gear mechanism has a planetary gear mechanism, the sun gear of the planetary gear mechanism is connected to the input side, the ring gear is connected to the output side, the reverse brake that locks the carrier to the case, and the carrier and the sun gear.
- the thing provided with the direct connection clutch is disclosed. When moving forward, the reverse brake is engaged and the direct clutch is released, so that the driving force input to the input side is reversed and decelerated and transmitted to the output side. By releasing the, the input side and the output side are directly connected.
- the first shaft that supports the drive pulley of the belt-type continuously variable transmission the second shaft that supports the driven pulley, and the third shaft of the differential device. It becomes a structure. Therefore, the engine drive force is reversed by the forward / reverse switching device during forward travel and transmitted to the drive pulley, and the output shaft is driven from the driven pulley via the differential device, so that the output shaft is the same as the engine rotation direction during forward travel. Can be driven in the direction.
- a three-shaft configuration in this way, a simple and compact continuously variable transmission can be realized.
- the rotational speed of the drive pulley can be suppressed even during high-speed rotation of the engine, and loss torque can be reduced.
- FIG. 8 shows the structure of the forward / reverse switching device described in Patent Document 1.
- the sun gear 101 of the planetary gear mechanism 100 constituting the forward / reverse switching device is coupled to the input shaft 102, and the pinion gear 103 that meshes with the sun gear 101 is supported by the carrier 105 via the pinion shaft 104.
- On the front side of the carrier 105 is a disc-shaped carrier plate 106.
- the inner diameter side is rotatably supported by the input shaft 102, the outer diameter side is used as the brake hub 106a of the reverse brake 107, and the clutch pub 106b of the direct coupling clutch 108 is fixed to the middle part.
- the hydraulic piston 109 for fastening the clutch disk of the direct coupling clutch 108 is disposed in the clutch drum 110, and the inner peripheral end of the clutch drum 110 is connected to the input shaft 102.
- the hydraulic piston 111 for fastening the brake disk of the reverse brake 107 is accommodated in a recess 113 formed on the inner wall of the transmission case 112.
- the inner diameter of the ring gear 114 that meshes with the pinion gear 103 is spline-fitted inside the pulley shaft 116 of the drive pulley 115! /
- the clutch drum 110 in order to connect the clutch drum 110 to the input shaft 102, the clutch drum 110 must be machined into a multi-stage bent shape, the structure is complicated, the machining cost is high, and torque transmission is also favorable. There is a problem.
- Patent Document 2 The same problem as in Patent Document 1 also occurs in a continuously variable transmission as described in Patent Document 2.
- This continuously variable transmission has a four-shaft configuration, and a forward / reverse switching device is provided between the input shaft and the drive pulley, and power is transferred from the driven pulley to the differential device via the reduction gear. Is transmitted.
- the forward / reverse switching device includes a double pinion type planetary gear mechanism, a direct coupling clutch provided between the input shaft and the carrier, and a reverse rotation brake provided between the ring gear and the transmission case.
- the sun gear is coupled to the input shaft on the input side
- the carrier is coupled to the drive pulley on the output side.
- the input shaft and the drive pulley are directly connected by fastening the direct clutch, and the rotation of the input shaft is transmitted to the drive pulley as it is, and is transmitted to the differential device via the driven pulley and the reduction gear.
- fasten the reverse brake When reversing, fasten the reverse brake.
- the rotation of the input shaft is reversed and transmitted to the drive pulley, and is transmitted to the differential device via the driven pulley and the reduction gear.
- Patent Document 2 Japanese Patent Laid-Open No. 10-184834
- an object of the present invention is to provide a forward / reverse switching device for a small continuously variable transmission with a simple structure by reducing friction loss by providing a hydraulic actuator for a direct coupling clutch on a stationary member.
- the present invention comprises a planetary gear mechanism, a reverse brake, and a direct coupling clutch, wherein the sun gear of the planetary gear mechanism is coupled to the input member, and one of the carrier and the ring gear serves as the output member.
- the reverse brake is provided between the other of the carrier and the ring gear and the transmission case
- the direct clutch is provided between the carrier and the sun gear or the input member, and is directly connected to the reverse brake.
- the hydraulic actuator for engaging the direct coupling clutch is fixed to the transmission case or the transmission case. Between the piston of the hydraulic actuator and the clutch disk of the direct coupling clutch.
- the axial pressure allows rolling to provide a reverse switching exchange device before the continuously variable transmission, characterized in that it is arranged a thrust bearing to reach Den.
- a single-pione planetary gear mechanism is used, the ring gear of the planetary gear mechanism is coupled to the output member, a reverse brake is provided between the carrier and the transmission case, and a direct clutch is provided between the carrier and the sun gear.
- a reverse brake is provided between the carrier and the transmission case
- a direct clutch is provided between the carrier and the sun gear.
- the hydraulic actuator for fastening the direct coupling clutch is provided on the stationary member, it is possible to reduce the friction loss that does not require the provision of a seal ring for preventing oil leakage in the oil supply passage to the clutch. Also, since the hydraulic actuator does not generate centrifugal hydraulic pressure due to rotation, hydraulic control is simplified, and there is no need to provide a check ball for discharging the centrifugal hydraulic pressure to the piston. Since it is only necessary to form the hydraulic chamber directly in a stationary member such as a transmission case, there is an advantage that a clutch drum having a complicated shape can be omitted, the structure can be simplified, and the processing cost can be reduced.
- the hydraulic piston does not rotate because the hydraulic actuator is provided on the stationary member. Therefore, when the hydraulic piston is pressed against the clutch disk of the direct coupling clutch, relative rotation occurs between them. Therefore, a thrust bearing is arranged between the clutch disc and the hydraulic piston. Thus, the axial pressure of the piston is effectively transmitted to the clutch disk, and the piston is prevented from rotating with the clutch disk.
- the clutch disk includes both a friction disk and a plate member.
- the thrust bearing any bearing such as a roller bearing or a ball bearing may be used as long as it allows relative rotation between the piston and the clutch disk and transmits an axial force.
- the carrier of the planetary gear mechanism is coupled to the output member, a reverse brake is provided between the ring gear and the transmission case, and a direct clutch is provided between the carrier and the sun gear. It can also be provided.
- the forward drive state is established by engaging the direct clutch and releasing the reverse brake
- the reverse drive state is established by engaging the reverse brake and releasing the direct clutch.
- a continuously variable transmission with a 4-axis configuration can be realized.
- Table 1 shows forward and backward travel using two types of planetary gear mechanisms: single pion and double pion. This shows the difference between the switching devices.
- the cylinder portion of the hydraulic actuator for fastening the direct coupling clutch is formed on the back surface portion of the oil pump cover fixed to the transmission case and disposed adjacent to the direct coupling clutch in the axial direction. .
- an oil pump cover fixed to the transmission case may be located adjacent to the front side of the direct coupling clutch. If the cylinder portion of the hydraulic actuator is formed on the back side of the oil pump cover, the cylinder portion can be buried in the oil pump cover, and the axial dimension can be shortened.
- the carrier has an outer spline on the outer periphery that engages with the inner periphery of the brake disc of the reverse brake, and an inner periphery that has a cylindrical portion that has an inner spline that engages with the outer periphery of the clutch disk of the direct coupling clutch. It is good to provide. That is, it is desirable to provide the carrier with a cylindrical portion that serves both as a brake hub for the reverse brake and a clutch drum for the direct coupling clutch.
- Patent Document 1 a disk-shaped carrier plate is fixed to the front side of the carrier, and the inner diameter side of the carrier plate is rotatably supported by the input shaft.
- the clutch pub of the direct coupling clutch is fixed to the intermediate part.
- the carrier is provided with a cylindrical part that serves as both a brake hub and a clutch drum, only one cylindrical part is required, and the mechanical strength of the cylindrical part can be easily secured as well as the structure is simplified. Torque transmission performance is improved.
- the outer spline and the inner spline are formed so as to overlap in the axial direction, the axial dimension of the forward / reverse switching device including the carrier, the direct coupling clutch and the reverse brake can be further shortened.
- a missing tooth portion lacking an inner spline is provided on the inner circumference of the cylindrical portion of the carrier, and a pion hole for supporting the pion shaft is formed at a position corresponding to the missing tooth portion and the circumferential direction.
- the radial distance R between the pion hole and the bottom surface of the tooth missing portion should be smaller than the height T of the inner spline.
- the pion hole can be formed at a position close to the inner peripheral surface of the cylindrical portion, the dimension in the radial direction of the forward / reverse switching device can be shortened.
- the sun gear may be provided with a cylindrical portion having an outer spline that engages with the inner peripheral portion of the clutch disk of the direct coupling clutch. That is, it is preferable to provide a cylindrical portion that serves as a clutch hub of the direct coupling clutch.
- Patent Document 1 a direct coupling clutch is provided between a clutch drum connected to an input shaft and a carrier. Therefore, a complicatedly shaped clutch drum is required, and the structure of the direct clutch is complicated and occupies a large space.
- the clutch drum is brought into synergy with the cylindrical part of the carrier.
- a stationary member disposed at a position facing the hydraulic piston with the brake disk of the reverse brake interposed therebetween is used.
- the stationary member is arranged on the front side (engine side) of the planetary gear mechanism.
- an oil pump cover can be used as such a stationary member.
- the brake disc includes both a friction disc and a plate member.
- a stagger portion for supporting an axial end portion of the clutch disk of the direct coupling clutch is provided on the carrier of the planetary gear mechanism.
- the hydraulic actuator for fastening the direct clutch is provided on the stationary member, it is necessary to provide a seal ring for preventing oil leakage in the oil supply passage to the clutch. The friction loss can be reduced. Also, since the hydraulic actuator does not generate centrifugal hydraulic pressure due to rotation, hydraulic control is simplified, and it is not necessary to provide a check ball for discharging the centrifugal hydraulic pressure to the piston. Such as transmission case Since it is only necessary to form a hydraulic chamber in the stationary member, there is an advantage that a complicated shape of the clutch drum can be omitted and the processing cost can be reduced.
- FIG. 1 is a developed sectional view of an example of a continuously variable transmission according to the present invention.
- FIG. 2 is a skeleton diagram of the continuously variable transmission shown in FIG.
- FIG. 3 is a detailed sectional view of the forward / reverse switching device for the continuously variable transmission shown in FIG.
- FIG. 4 is a front view of a planetary gear mechanism of a forward / reverse switching device.
- FIG. 5 is a cross-sectional view taken along line V—V in FIG.
- FIG. 6 is a cross-sectional view taken along line VI—VI in FIG.
- FIG. 7 is a skeleton diagram of a second embodiment of the forward / reverse switching device according to the present invention.
- FIG. 8 is a cross-sectional view of a conventional forward / reverse switching device for a continuously variable transmission.
- 1 to 3 show an example of a continuously variable transmission according to the present invention.
- the continuously variable transmission of this embodiment is an FF horizontal type automotive transmission, which is roughly switched between forward and reverse rotation of the input shaft 3 and the input shaft 3 driven by the engine output shaft 1 via the torque converter 2.
- the forward / reverse switching device 4 that transmits to the drive shaft 10, the continuously variable transmission A consisting of the drive pulley 11, the driven pulley 21, and the V belt 15 wound between both pulleys, the power of the driven shaft 20 as the output shaft It consists of a differential device 30 that transmits to 32.
- the input shaft 3 and the drive shaft 10 are arranged on the same axis, and the driven shaft 20 and the output shaft 32 of the differential device 30 are arranged parallel to the input shaft 3 and non-coaxially. Therefore, this continuously variable transmission has a three-axis configuration as a whole.
- the V belt 15 used in this embodiment is a known metal belt composed of a pair of endless tension bands and a number of blocks supported by these tension bands.
- Each component constituting the continuously variable transmission is accommodated in a transmission case 5.
- An oil pump 6 is disposed between the torque converter 2 and the forward / reverse switching device 4.
- the oil pump includes an oil pump body 7 fixed to the transmission case 5,
- An oil pump cover 8 fixed to the oil pump body 7 and a pump gear 9 accommodated between the oil pump body 7 and the oil pump cover 8 are configured.
- the pump gear 9 is driven by the pump impeller 2a of the torque converter 2.
- the turbine runner 2b of the torque converter 2 is connected to the input shaft 3, and the stator 2c is supported by the transmission case 5 via a one-way clutch 2d.
- the forward / reverse switching device 4 includes a planetary gear mechanism 40, a reverse brake 50, and a direct coupling clutch 51, and an input shaft in which the sun gear 41 of the planetary gear mechanism 40 is an input rotating member. 3 and the ring gear 42 is connected to the drive shaft 10 which is an output rotating member.
- the planetary gear mechanism 40 is a single pion system
- the reverse brake 50 is provided between the carrier 44 supporting the pinion gear 43 and the transmission case 5
- the direct clutch 51 is provided between the carrier 44 and the sun gear 41. It has been.
- the direct clutch 51 is released and the reverse brake 50 is engaged, the rotation of the input shaft 3 is reversed and decelerated and transmitted to the drive shaft 10.
- the reverse brake 50 is released and the direct clutch 51 is engaged, the carrier 44 and the sun gear 41 of the planetary gear mechanism 40 rotate together, so that the input shaft 3 and the drive shaft 10 are directly connected.
- the drive pulley 11 of the continuously variable transmission A is freely movable in the axial direction via a fixed sheave 11a formed integrally on a drive shaft (pulley shaft) 10 and a roller spline portion 13 on the drive shaft 10. And a movable sheave l ib supported so as to be integrally rotatable, and a hydraulic servo 12 provided behind the movable sheave l ib.
- a piston portion 12a extending to the rear side is formed on the outer peripheral portion of the movable sheave rib, and the outer peripheral portion of the piston portion 12a is in sliding contact with the inner peripheral portion of the cylinder 12b fixed to the drive shaft 10.
- a hydraulic fluid chamber 12c of the hydraulic servo 12 is formed between the movable sheave l ib and the cylinder 12b, and the shift control is performed by controlling the hydraulic pressure to the hydraulic fluid chamber 12c.
- the driven pulley 21 has a fixed sheave 21a formed integrally on the driven shaft (pulley shaft) 20 and a roller spline portion 23 on the driven shaft 20 so as to be axially movable and integrally rotatable.
- the movable sheave 21b is supported by the hydraulic sheave 21 and the hydraulic servo 22 is provided behind the movable sheave 21b.
- the structure of this roller spline portion 23 is the roller spline of the drive pulley 11. This is the same as the unit 13.
- a cylinder portion 22a extending to the rear side is formed on the outer peripheral portion of the movable sheave 21b, and a piston 22b fixed to the driven shaft 20 is in sliding contact with the inner peripheral portion of the cylinder portion 22a.
- a hydraulic oil chamber 22c of the hydraulic servo 22 is formed between the movable sheave 21b and the piston 22b.
- One end of the driven shaft 20 extends toward the engine side, and an output gear 27 is fixed to the one end.
- the output gear 27 meshes with the ring gear 31 of the differential device 30, and power is transmitted from the differential device 30 to the output shaft 32 extending left and right to drive the wheels.
- the carrier 44 includes a disc-shaped carrier flange 45 and an annular carrier rim 46.
- the inner diameter portion of the carrier flange 45 extends between the sun gear 41 and the ring gear 42 in the inner diameter direction, and is connected to the input shaft 3. It is supported rotatably.
- the carrier flange 45 is formed with a plurality of (in this case, six) columnar portions 45a projecting in the axial direction toward the carrier rim 46, and the above-described pion gear 43 is formed in the space between the columnar portions 45a. Is arranged.
- the front end surface of the columnar portion 45a and the carrier rim 46 are metal-bonded by sintering, and the carrier flange 45 and the carrier rim 46 are integrally fixed. It may be fixed by welding, brazing or screwing.
- pinion holes 45b, 46a are formed at the opposed positions of the carrier flange 45 and the carrier rim 46, and the pinion gear 43 is supported in these pinion holes 45b, 46a.
- the pinion shaft 47 to be inserted is inserted over the bridge!
- Thrust washers 43a are arranged between the pinion gear 43 and the carrier flange 45 and between the pinion gear 43 and the carrier rim 46, respectively.
- a one-dollar bearing 43b is disposed in a gap between the inner periphery of the pion gear 43 and the outer periphery of the pion shaft 47, and the pion gear 43 is rotatable with respect to the pion shaft 47.
- the carrier rim 46 is formed with a cylindrical portion 46 b that protrudes in the axial direction toward the front side (engine side), and this cylindrical portion 46 b is formed in the reverse brake 50. It serves as both a clutch hub and a clutch drum for the direct clutch 51. That is, an outer spline 46c is formed on the outer peripheral portion of the cylindrical portion 46b to engage the inner diameter portion of the brake disc 50a of the reverse brake 50, and the outer diameter portion of the clutch disc 51a of the direct clutch 51 is engaged on the inner peripheral portion. An inner spline 46d is formed.
- the spline 46c and 46d forces are provided on the inner and outer peripheral surfaces of the cylindrical portion 46b in the radially opposite positions, and both splines overlap in the axial direction in the space S, so the axial dimension is shortened accordingly. it can. Further, since the reverse brake 50 and the direct coupling clutch 51 can be disposed on the inner and outer circumferences of the cylindrical portion 46b, the radial space can be shortened.
- the inner peripheral surface of the cylindrical portion 46b of the carrier rim 46 is formed with a notch portion 46e lacking the inner spline 46d at a predetermined interval.
- the hole 46a is formed at a position corresponding to the missing tooth portion 46e in the circumferential direction.
- the radial distance R between the pinion hole 46a and the bottom surface of the missing tooth portion 46e is smaller than the height T of the inner spline 46d.
- the pion hole 46a can be formed at a position close to the inner peripheral surface of the cylindrical portion 46b, and the radial dimension of the forward / reverse switching device 4 can be shortened.
- the piston 50b of the reverse brake 50 is accommodated in a concave hydraulic chamber 50c formed on the inner wall of the transmission case 5, and the piston 50b is supplied by the hydraulic pressure supplied to the hydraulic chamber 50c. Is actuated to engage the brake disc 50a.
- a cylindrical stopper portion 8a protrudes from the oil pump cover 8, which is a stationary member, as a reaction member that supports the end of the brake disc 50a pressed by the pressure of the piston 50b. Therefore, the snap ring that supports the end of the brake disc 50a can be omitted.
- a cylindrical portion 41a which serves as a clutch hub of the direct coupling clutch 51, protrudes from the body, and a direct coupling clutch is provided on the outer periphery of the cylindrical portion 41a.
- the inner diameter of 51 clutch disc 5 la is supported.
- a concave hydraulic chamber 51b is formed on the back side (forward / reverse switching device side) of the oil pump cover 8, and this hydraulic chamber 51b
- the piston 51c is actuated by the hydraulic pressure supplied to the direct clutch 51, and the direct clutch 51 is fastened.
- the piston 51c has a U-shaped cross section, and a thrust bearing 52 that allows relative rotation is attached to the side surface of the piston 51c that faces the clutch disc 5la. Therefore, the axial pressure of the piston 51c is effectively transmitted to the clutch disk 51a, and the piston 51c is prevented from rotating with the clutch disk 51a of the direct coupling clutch 51. Since the carrier 44 (carrier rim 46) is disposed behind the clutch disc 51a, the end of the clutch disc 5 la pushed by the piston 5 lc is positioned at the end surface of the carrier 44 (side surface of the carrier rim 46). Can be supported and can eliminate snap rings and special reaction force members
- the forward / reverse switching device 4 has a hydraulic actuator for fastening the direct clutch 51 provided on the oil pump cover 8 which is a stationary member! /. Therefore, oil leakage prevention is provided in the supply oil path to the hydraulic actuator. Friction loss can be reduced without the need for a seal ring.
- the clutch drum having a complicated shape can be omitted, the structure can be simplified, and the processing cost can be reduced.
- the carrier 44 is provided with a cylindrical portion 46b that doubles as the brake hub of the reverse brake 50 and the clutch drum of the direct coupling clutch 51, it is only necessary to provide one cylindrical portion 46b on the carrier, and the structure is simplified. As a result, the mechanical strength of the cylindrical portion 46b can be easily secured. Furthermore, a useless space in the radial direction is not generated. Furthermore, since the sun gear 41 is provided with a cylindrical portion 41a that serves as a clutch hub of the direct coupling clutch 51, the structure of the direct coupling clutch 51 can be further simplified, the number of components can be reduced, and the forward / reverse switching device can be further compacted. It becomes possible.
- FIG. 7 shows a second embodiment of the forward / reverse switching device according to the present invention.
- the same parts as those in the first embodiment are denoted by the same reference numerals, and redundant description is omitted.
- the configuration other than the forward / reverse switching device is the same as that of Patent Document 2.
- This planetary gear mechanism 40 ′ is of a double beon type, and two types of pions 43A and 43B are supported on a carrier 44.
- One pinion 43A meshes with the ring gear 42 and the pinion 43B, and the other pinion 43B meshes with the pinion 43A and the sun gear 41.
- the sun gear 41 is coupled to the input shaft 3, and the carrier 44 is coupled to the drive shaft 10.
- the reverse brake 50 is provided between the ring gear 42 and the transmission case 5, and the hydraulic piston 50 b for operating the reverse brake 50 is disposed in the transmission case 5.
- the direct coupling clutch 51 is provided between the carrier 44 and the sun gear 41, and a hydraulic piston 51 c for operating the direct coupling clutch 51 is accommodated in the oil pump cover 8.
- a thrust bearing 52 is disposed between the hydraulic piston 51c and the clutch disk of the direct clutch 51.
- the direct coupling clutch 51 is provided between the carrier 44 and the sun gear 41 between the carrier 44 and the input shaft 3, the clutch drum having a complicated shape can be omitted, the structure can be simplified, and the compact A direct clutch 51 can be configured.
- the columnar portion 45a is integrally formed with the carrier flange 45 of the planetary gear mechanism 40, and the annular carrier rim 46 is fixed to the end of the columnar portion 45a. It may be provided on the rim 46 side and the carrier flange 45 may be fixed to the end of the columnar part.
- the cylinder portion of the hydraulic actuator for fastening the direct coupling clutch 51 can be provided directly on the power transmission case 5 formed on the oil pump cover 8. It can also be provided on a stationary member other than the oil pump cover 8.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Transmission Devices (AREA)
- Structure Of Transmissions (AREA)
- General Details Of Gearings (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP05805253A EP1808619B1 (en) | 2004-11-02 | 2005-10-25 | Forward-reverse switching device for stepless speed changer |
JP2006543149A JP4597138B2 (ja) | 2004-11-02 | 2005-10-25 | 無段変速機の前後進切替装置 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004-318661 | 2004-11-02 | ||
JP2004318661 | 2004-11-02 |
Publications (1)
Publication Number | Publication Date |
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WO2006049034A1 true WO2006049034A1 (ja) | 2006-05-11 |
Family
ID=36319048
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/019545 WO2006049034A1 (ja) | 2004-11-02 | 2005-10-25 | 無段変速機の前後進切替装置 |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP1808619B1 (ja) |
JP (1) | JP4597138B2 (ja) |
KR (1) | KR100877277B1 (ja) |
CN (1) | CN100470095C (ja) |
WO (1) | WO2006049034A1 (ja) |
Cited By (5)
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JP2009133395A (ja) * | 2007-11-30 | 2009-06-18 | Aisin Aw Industries Co Ltd | 無段変速装置を備えた車輌 |
CN101265969B (zh) * | 2007-03-12 | 2012-12-05 | 通用汽车环球科技运作公司 | 变速器组件 |
JP5689163B1 (ja) * | 2013-11-18 | 2015-03-25 | 株式会社小松製作所 | キャリア、遊星歯車機構、トランスミッション、及び作業車両 |
JP2015194235A (ja) * | 2014-03-31 | 2015-11-05 | アイシン・エィ・ダブリュ株式会社 | プラネタリギア |
CN107642590A (zh) * | 2016-07-20 | 2018-01-30 | 株式会社神崎高级工机制作所 | Hmt构造 |
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JP4293263B2 (ja) * | 2007-04-19 | 2009-07-08 | トヨタ自動車株式会社 | 車両用動力伝達装置 |
KR100930548B1 (ko) * | 2007-10-02 | 2009-12-09 | 현대자동차주식회사 | 무단변속기의 인풋샤프트 및 풀리 연결구조 |
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- 2005-10-25 WO PCT/JP2005/019545 patent/WO2006049034A1/ja active Application Filing
- 2005-10-25 JP JP2006543149A patent/JP4597138B2/ja not_active Expired - Fee Related
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CN101265969B (zh) * | 2007-03-12 | 2012-12-05 | 通用汽车环球科技运作公司 | 变速器组件 |
JP2009133395A (ja) * | 2007-11-30 | 2009-06-18 | Aisin Aw Industries Co Ltd | 無段変速装置を備えた車輌 |
JP5689163B1 (ja) * | 2013-11-18 | 2015-03-25 | 株式会社小松製作所 | キャリア、遊星歯車機構、トランスミッション、及び作業車両 |
WO2015072180A1 (ja) * | 2013-11-18 | 2015-05-21 | 株式会社小松製作所 | キャリア、遊星歯車機構、トランスミッション、及び作業車両 |
US9909661B2 (en) | 2013-11-18 | 2018-03-06 | Komatsu Ltd. | Carrier, planetary gear mechanism, transmission, and working vehicle |
JP2015194235A (ja) * | 2014-03-31 | 2015-11-05 | アイシン・エィ・ダブリュ株式会社 | プラネタリギア |
CN107642590A (zh) * | 2016-07-20 | 2018-01-30 | 株式会社神崎高级工机制作所 | Hmt构造 |
CN107642590B (zh) * | 2016-07-20 | 2020-09-11 | 株式会社神崎高级工机制作所 | Hmt构造 |
Also Published As
Publication number | Publication date |
---|---|
EP1808619A4 (en) | 2010-09-08 |
JP4597138B2 (ja) | 2010-12-15 |
EP1808619B1 (en) | 2012-09-05 |
EP1808619A1 (en) | 2007-07-18 |
JPWO2006049034A1 (ja) | 2008-05-29 |
KR20070058001A (ko) | 2007-06-07 |
CN101048608A (zh) | 2007-10-03 |
CN100470095C (zh) | 2009-03-18 |
KR100877277B1 (ko) | 2009-01-07 |
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