JP4830709B2 - Planetary gear mechanism and vehicle transmission - Google Patents

Description

  The present invention relates to a planetary gear mechanism and a vehicle transmission using the planetary gear mechanism. The planetary gear mechanism employs a centrifugal oil supply system in which a multi-plate friction engagement device is disposed on the outer side of the ring gear and oil discharged from the oil supply passage of the sun gear is supplied to the multi-plate friction engagement device side. ing.

  In recent years, for vehicle transmissions, for example, a belt-type continuously variable transmission mechanism and a forward / reverse switching device disposed on the input side of the continuously variable transmission mechanism are used to reduce weight and size. There is.

  Here, a conventional forward / reverse switching device will be described with reference to FIGS. The forward / reverse switching device 80 mainly includes a planetary gear mechanism 81, a forward clutch 82, and a reverse brake 83.

  The planetary gear mechanism 81 mainly includes a sun gear 91, a ring gear 92, a large number of inner diameter side pinion gears 93, a large number of outer diameter side pinion gears 94, and a carrier 95. In the illustrated example, the sun gear 91 is integrally formed on one end side of the input shaft 79.

  Due to the relation that the meshing portions of the gears 91 to 94 of the planetary gear mechanism 81 are helical teeth, a thrust force is generated as the ring gear 92 rotates, and the ring gear 92 slides in the axial direction. Therefore, in order to position the ring gear 92 by restricting the slide in the axial direction, a positioning member 96 is integrally attached to the ring gear 92, and the inner diameter side of the radially inward flange 96b of the positioning member 96 is not provided. The primary pulley of the step transmission mechanism (not shown) is brought into contact with the end face of the cylindrical boss portion of the fixed sheave 70, and the inner diameter side of the radially inward flange 96 b is connected to the diameter of the carrier 95 via the thrust roller bearing 97. It is configured to abut against the outer surface of the direction outward flange 95b.

  The positioning member 96 has a shape in which a radially inward flange 96b is provided on one end side in the axial direction of the outer cylinder portion 96a, and is manufactured by, for example, pressing a metal plate. The outer cylindrical portion 96a of the positioning member 96 is formed in a wave shape in the circumferential direction. After the ring gear 95 is spline fitted to the inner diameter side spline of the outer cylindrical portion 96a, a snap ring is attached to the spline fitting portion. The positioning member 96 and the ring gear 92 are integrally coupled by attaching the 98 and making it non-separable in the axial direction.

  The forward clutch 82 and the reverse brake 83 are, for example, a wet multi-plate friction engagement device having a configuration in which a large number of inner diameter side friction plates 82a and 83a and outer diameter side friction plates 82b and 82b are alternately arranged in the axial direction. It has been.

  In the forward clutch 82, the inner diameter friction plate 82 a is spline-fitted to the outer diameter side spline of the carrier 95, and the outer diameter side friction plate 82 b is integrally attached to the sun gear 91. The cylinder member 85a is splined to the inner diameter side. As the operation of the forward clutch 82, the carrier 95 can be rotated relative to the sun gear 91 when the inner diameter side friction plate 82a and the outer diameter side friction plate 82b are disengaged by the hydraulic actuator 85. On the other hand, when the inner diameter side friction plate 82 a and the outer diameter side friction plate 82 b are brought into an engaged state, the carrier 95 can be brought into a locked state in which the carrier 95 can rotate integrally with the sun gear 91.

  In the reverse brake 83, the inner diameter side friction plate 83 a is spline fitted to the outer diameter side spline of the outer cylinder portion 96 a of the positioning member 96, and the outer diameter side friction plate 83 b is integrated with the transmission case 86. It is attached. As the operation of the reverse brake 83, when the inner diameter side friction plate 83a and the outer diameter side friction plate 83b are disengaged by the hydraulic actuator 87, the ring gear 92 is set in a free state in which it can rotate. On the other hand, when the inner diameter side friction plate 83a and the outer diameter side friction plate 83b are brought into an engaged state, the ring gear 92 can be brought into a locked state in which it cannot rotate.

  The sun gear 91 is provided with an oil supply path 100 along the central axis in a region from one end surface to the middle in the axial direction. Discharge ports 101 for discharging oil outward in the radial direction are provided at several circumferential positions at a plurality of positions in the longitudinal direction of the oil supply path 100.

  Although such an oil supply path 100 of the sun gear 91 is not shown, oil supplied from an oil pump installed in the vehicle transmission is blown outward in the radial direction by the rotational centrifugal force of the sun gear 91. As shown by the thick line arrows in FIG. 10, it is provided to be supplied between the contact portions of the components 91 to 96 of the planetary gear mechanism 81 and the friction plates 83 a and 83 b of the reverse brake 83. Such a form of oil supply is called a centrifugal oil supply system.

The oil discharged from the discharge port 101 on the most downstream side in the oil supply passage 100 of the sun gear 91 is the continuously variable transmission side, the radially inward flange 96b of the positioning member 96, and the radially outward flange of the carrier 95. It is supplied to a thrust roller bearing 97 interposed between them and 95b. In order to guide the oil that has passed through the thrust roller bearing 97 between the friction plates 83 a and 83 b of the reverse brake 83, a passage 105 that penetrates the outer cylindrical portion 96 a of the positioning member 96 inward and outward in the radial direction. (For example, refer to Patent Document 1).
Japanese Patent Laid-Open No. 2004-44723 (see, for example, FIG. 6)

  In the above conventional example, the passage 105 provided in the outer cylinder portion 96a of the positioning member 96 extends along the radial direction so as to connect the crest 96c of the outer diameter side spline of the outer cylinder portion 96a and the groove bottom of the inner diameter side spline. Therefore, even if oil is supplied to the inner periphery of the outer cylindrical portion 96a of the positioning member 96, at most, the outer diameter side where the passage 105 is installed among the numerous grooves of the inner diameter side spline. It is considered that only the oil that has reached the groove located on the inner diameter side of the spline crest 96c is guided to the reverse brake 83 side. Therefore, in the above conventional example, there is a concern that the oil supply to the reverse brake 83 becomes insufficient. There is room for improvement here.

  The present invention employs a centrifugal oil supply system in which a multi-plate friction engagement device is disposed on the outer diameter side of the ring gear and oil discharged from the oil supply passage of the sun gear is supplied to the multi-plate friction engagement device side. Another object of the present invention is to enable oil to be efficiently supplied to a multi-plate frictional engagement device while having a low-cost configuration.

In the present invention, a multi-plate frictional engagement device for switching between a free state in which the ring gear can be rotated and a locked state in which the ring gear cannot be rotated is disposed on the outer diameter side of the ring gear, and the sun gear is provided. A planetary gear mechanism that employs a centrifugal oil supply system that supplies oil discharged from an oil supply path to the multi-plate frictional engagement device side by the rotational centrifugal force of a sun gear, wherein the ring gear is arranged on the outer periphery thereof. A cylindrical thick member to which the inner diameter side friction plate of the plate type frictional engagement device is integrally attached is provided, and a positioning plate for positioning the ring gear in the axial direction is attached to one side surface of the ring gear. The one side surface of the ring gear and the positioning plate are separated from each other in the axial direction, so that the separation gap is formed as an annular gap continuous in the circumferential direction, and the ring gear is discharged from the oil supply passage of the sun gear. A passage for guiding the oil centrifugally supplied to the annular gap to the multi-plate friction engagement device side is provided, and the passage is an oblique hole that opens to a side surface and an outer diameter side of the ring gear; The gear and the inner diameter side friction plate are coupled to each other via a spline so as to be integrally rotatable, and at least one spline tooth in the outer diameter side spline of the ring gear is eliminated, and the outer diameter side opening of the passage is formed in the missing tooth portion. And the positioning plate and the carrier are brought into contact with an outer surface of a radially outward flange provided on a carrier supporting a plurality of pinion gears via a thrust roller bearing. The gap in the axial direction with the radially outward flange is a relay path for guiding oil from the oil supply path to the annular space, and the center of the carrier The carrier has a hollow shape, the center shaft portion is fitted on one end side of the sun gear in a relatively rotatable state, and the discharge port of the oil supply passage is disposed on one end side of the sun gear. a central shaft portion and the diametrically opposed gap between the sun gear and the discharge port is the upstream portion and which do characterized Rukoto refueling path when guiding the oil into the annular space from the oil supply passage.

  According to this configuration, when the oil discharged from the oil supply passage provided in the sun gear reaches the annular gap by the rotational centrifugal force of the sun gear, the oil flows into the ring gear passage and is on the outer diameter side of the ring gear. It will be guide | induced to the site | part in which a multi-plate type frictional engagement apparatus exists.

  Here, since the side opening in each passage is opened to the annular gap, the oil that has reached the annular gap flows in the circumferential direction with the rotation of the carrier, but the annular gap is circumferential. Since it is continuous in the direction, the oil present in the annular gap easily flows into the side surface side opening of the passage.

  For this reason, the oil centrifugally supplied from the oil supply passage of the sun gear to the annular gap can be efficiently guided to the multi-plate friction engagement device on the ring gear outer diameter side. It becomes possible to contribute to improvement of wear resistance between friction plates and long-term stabilization of engagement performance in the apparatus.

  In addition, the ring gear is formed as a thick cylindrical member, the inner diameter side friction plate of the multi-plate friction engagement device is attached to the outer diameter side, and the positioning plate is attached to the side surface of the ring gear. Therefore, the number of parts and assembly man-hours can be reduced compared to the conventional example in which the ring gear is assembled to the positioning member to which the friction plate on the inner diameter side of the reverse brake is attached and then secured with a snap ring. It will be possible to contribute to cost reduction.

  In this configuration, since the oil passage made of an oblique hole is provided in the ring gear that is the thick cylindrical member described above, an annular gap having a shape that is continuous in the circumferential direction is provided between the ring gear and the positioning plate. Is possible. Thereby, it becomes possible to improve the oil supply efficiency with respect to the multi-plate friction engagement device side arranged on the ring gear outer diameter side.

  Also, if the passage is an oblique hole, both the side surface opening and the outer peripheral surface side opening have an elliptical shape, so that, for example, the opening area is larger than the circular hole formed in the radial direction, and the oil inflow efficiency is increased. This is advantageous for increasing the oil discharge efficiency.

Further, in the present invention, the ring gear and the inner diameter side friction plate are coupled to each other via a spline so as to be integrally rotatable, and at least one spline tooth in the outer diameter side spline of the ring gear is eliminated. The outer diameter side opening of the passage is arranged .

By providing a passage in the missing tooth portion as in this configuration, when a passage having as large an opening as possible is formed , it is advantageous in increasing the oil inflow efficiency and the oil discharge efficiency.

In the present invention, by the inner surface of the positioning plates is abutted via a thrust roller bearing on the outer surface of the radially outward flange provided on the carrier that supports the plurality of pinion gears, said positioning plate axially facing gap between the radially outwardly flange of the carrier Ru Tei is a relay path for guiding the oil into the annular gap from the oil supply passage.

Here, by specifying the installation state of the positioning plate for positioning the ring gear, the axial direction facing the gap between the radially outward flange of the positioning plate and the carrier, the oil from the oil supply passage of the sun gear to the annular gap the is to clarify Rukoto is a relay route for guiding, the conformity structure to thereby embodiment.

In the present invention, the center shaft portion of the carrier supporting the plurality of pinion gears is hollow, and the center shaft portion is externally fitted to the one end side of the sun gear so as to be relatively rotatable, and one end side of the sun gear. When the discharge port of the oil supply path is disposed in the radial direction gap between the center shaft portion of the carrier and the sun gear, and the discharge port guides oil from the oil supply path to the annular gap. Ru Tei is the upstream portion of the fuel supply path.

This Kodewa, as the upstream portion of the fuel supply path when guiding the oil from the oil supply passage of the sun gear to the annular gap, utilizing the diametrically opposed portion of the inner surface and the outer peripheral surface of the sun gear of the central axis of the carrier Thus, the structure conforms to the embodiment.

In addition, the present invention provides a forward / reverse switching device for setting the rotational power input from the internal combustion engine as necessary to output the vehicle in the same rotational direction or the vehicle reverse state in which the rotational power is reversed and output in the reverse rotational direction. a vehicle transmission having the the forward-reverse switching apparatus, comprising a Yu star gear mechanism having the above structure, a multi-plate friction engagement device for forward, and a multi-plate friction engagement device for reverse , wherein the sun gear in the planetary gear mechanism is an input shaft of the rotational power from the internal combustion engine, the center axis of the carrier are the output shaft, further, a multi-plate friction engagement device for forward, the planetary gears An inner diameter friction plate that is integrally attached to the carrier outer diameter side of the mechanism, an outer diameter side friction plate that is integrally attached to the inner diameter side of a member that is rotatably attached to the sun gear of the planetary gear mechanism, and the carrier. And an actuator to switch the A locked to a free state or integrally rotatable to rotate relative to said sun gear, a multi-plate friction engagement device for the reverse, the ring gear outer diameter side of the planetary gear mechanism An inner diameter friction plate that is integrally attached to the transmission case, an outer diameter friction plate that is integrally attached to the transmission case, and an actuator that switches the ring gear to a free state in which the ring gear can rotate or a locked state in which the ring gear cannot rotate. It is characterized by having.

  In this configuration, the forward / reverse switching device provided in the vehicle transmission is configured by the planetary gear mechanism as described above, and the multi-plate frictional engagement device disposed on the outer diameter side of the ring gear of the planetary gear mechanism is moved backward. Specific for. As a result, the oil centrifugally supplied from the oil supply passage of the sun gear to the annular gap can be efficiently guided to the reverse gear multi-plate friction engagement device on the outer side of the ring gear. It becomes possible to contribute to improvement of wear resistance in the apparatus and long-term stabilization of the engagement performance.

  According to the present invention, it is possible to efficiently supply oil to a multi-plate frictional engagement device disposed on the outer side of the ring gear with a low-cost configuration.

  Embodiments of the present invention will be described below with reference to the drawings. 1 to 8 show an embodiment of the present invention. In this embodiment, an automatic transmission type is exemplified as a vehicle transmission.

  As shown in FIG. 1, a vehicular transmission 1 uses a rotational power (torque) input from an internal combustion engine (not shown) via a fluid coupling (torque converter) 2 as a forward / reverse switching device 3 and a continuously variable transmission mechanism. 4 and the differential 5 are transmitted to wheels (not shown).

  The fluid coupling 2, the forward / reverse switching device 3, the continuously variable transmission mechanism 4, and the differential 5 are housed in a split transmission case 6.

  Note that the fluid coupling 2 and the differential 5 are basically known configurations and are not directly related to the present invention, and thus detailed description thereof will be omitted.

  The continuously variable transmission mechanism 4 is basically a known configuration, but the belt 4C is wound around the primary pulley 4A and the secondary pulley 4B, and the winding diameter of the belt 4C around the pulleys 4A and 4B is increased or decreased. It is the structure which shifts by. The continuously variable transmission mechanism 4 is a so-called “CVT” of a belt type, but can be a toroidal continuously variable transmission mechanism, for example.

  The forward / reverse switching device 3 is a vehicle forward state (FIGS. 2 and 3) that outputs rotational power (torque) input from an internal combustion engine (not shown) through the fluid coupling 2 in the same rotational direction as necessary. (See FIG. 4 and FIG. 5).

  The forward / reverse switching device 3 mainly includes a planetary gear mechanism 20, a forward clutch 30, and a reverse brake 40, each having the following configuration.

  In this embodiment, the planetary gear mechanism 20 is a double-pinion type planetary gear mechanism, and mainly includes a sun gear 21 serving as an input shaft, a ring gear 22, a large number of inner side pinion gears 23 serving as a planetary gear, and a large number of planetary gear mechanisms. The outer diameter side pinion gear 24 and a carrier 25 serving as an output shaft are provided.

  The sun gear 21 is integrally formed on one end side of the input shaft 7. The ring gear 22 is arranged on the sun gear 21 so as to be concentric with it. The inner diameter side pinion gear 23 is disposed in a state in which the sun gear 21 and the outer diameter side pinion gear 24 are engaged with each other in the opposed annular space between the sun gear 21 and the ring gear 22. The outer diameter side pinion gear 24 is arranged in a state in which the inner diameter side pinion gear 23 and the ring gear 22 are engaged with each other in an opposed annular space between the sun gear 21 and the ring gear 22.

  The carrier 25 rotatably supports both pinion gears 23 and 24, and has a hollow central shaft portion 25a having a radially outward flange 25d at one end in the axial direction, and a radially outward direction of the central shaft portion 25a. A plurality of planetary shafts 25b which are integrally attached in a cantilevered state at several circumferential positions of the flange 25d, and are attached to the free end side of each planetary shaft 25b so as to be parallel to the radially outward flange 25d in the axial direction. It is the structure containing the annular plate 25c arrange | positioned facing.

  The center shaft portion 25a of the carrier 25 is spline-fitted into the cylindrical boss portion of the fixed sheave 4A1 of the primary pulley 4A of the continuously variable transmission mechanism 4, and the carrier 25 and the fixed sheave 4A1 are connected to be integrally rotatable. ing.

  The forward clutch 30 and the reverse brake 40 include, for example, a large number of inner diameter side friction plates 31 and 41 and outer diameter side friction plates 32 and 42 arranged alternately in the axial direction, and both friction plates are operated by hydraulic actuators 33 and 43. Is a wet multi-plate frictional engagement device configured to control the engagement state or the disengagement state. Although not shown, the hydraulic actuators 33 and 43 are controlled by a control device (ECU) mounted on the vehicle.

  In the forward clutch 30, the inner diameter side friction plate 31 is spline-fitted to the outer diameter side spline 25 e of the annular plate 25 c of the carrier 25, and the outer diameter side friction plate 32 is integrally attached to the sun gear 21. It is spline-fitted to the inner diameter side of 33 cylinder members 33a.

  As an operation of the forward clutch 30, when the inner diameter side friction plate 31 and the outer diameter side friction plate 32 are disengaged by the actuator 33, the carrier 25 is brought into a free state in which the carrier 25 can rotate relative to the sun gear 21. On the other hand, when the inner diameter side friction plate 31 and the outer diameter side friction plate 32 are brought into an engaged state, the carrier 25 can be brought into a locked state in which the carrier 25 can rotate integrally with the sun gear 21.

  In the reverse brake 40, the inner diameter side friction plate 41 is spline fitted to the outer diameter side spline 22 a of the ring gear 22, and the outer diameter side friction plate 42 is integrally attached to the transmission case 6. .

  As an operation of the reverse brake 40, when the inner diameter side friction plate 41 and the outer diameter side friction plate 42 are disengaged by the actuator 43, the ring gear 22 can be brought into a rotatable free state, When the inner diameter side friction plate 41 and the outer diameter side friction plate 42 are brought into the engaged state, the ring gear 22 can be brought into a locked state where it cannot rotate.

  Next, a basic operation of the above-described forward / reverse switching device 3 will be described.

  Examples of the shift position of the vehicle transmission 1 include a parking position, a reverse position, a neutral position, and a drive position.

  First, when the shift of the vehicle transmission 1 is at the drive position, the carrier 25 of the planetary gear mechanism 20 is moved to the input shaft 7 by engaging the forward clutch 30 of the forward / reverse switching device 3 as shown in FIG. The ring gear 22 of the planetary gear mechanism 20 is set in a free state where the planetary gear mechanism 20 is rotatable by bringing the reverse brake 40 into a non-engaged state while the sun gear 21 and the sun gear 21 are in a locked state.

  In this state, when the input shaft 7 and the sun gear 21 integrated therewith are rotated in the direction indicated by the solid line arrow as shown in FIG. 3 due to the rotational power of the internal combustion engine (not shown), the carrier 25 and the ring gear 22 are connected. The fixed sheave 4 </ b> A <b> 1 of the primary pulley 4 </ b> A of the continuously variable transmission mechanism 4 that rotates integrally and is spline-fitted with the carrier 25 rotates in the same rotational direction as the input shaft 7. At this time, the inner diameter side pinion gear 23, the outer diameter side pinion gear 24, the carrier 25, the sun gear 21, and the ring gear 22 are integrally rotated.

  As a result, the forward drive force is transmitted from the continuously variable transmission mechanism 4 to the wheels (not shown) via the differential 5.

  On the other hand, when the shift of the vehicle transmission 1 is in the reverse position, the carrier 25 of the planetary gear mechanism 20 is moved to the sun gear 21 by disengaging the forward clutch 30 of the forward / reverse switching device 3 as shown in FIG. On the other hand, the reverse gear 40 is brought into an engaged state while the ring gear 22 of the planetary gear mechanism 20 is brought into a non-rotatable locked state.

  In this state, when the input shaft 7 and the sun gear 21 integrated therewith rotate in the direction of the solid arrow as shown in FIG. 5 by the rotational power of the internal combustion engine (not shown), the inner diameter side pinion gear 23 and the outer diameter side The pinion gear 24 rotates and rolls (revolves) on the outer periphery of the sun gear 21 and the inner periphery of the ring gear 22, and the revolving direction of the pinion gears 23 and 24 and the carrier 25 rotate in the same direction. The rotation direction of the carrier 25 is opposite to the rotation direction of the input shaft 7.

  Since the carrier 25 that is reversed with respect to the rotation direction of the input shaft 7 in this way is integrally connected to the fixed sheave 4A1 of the primary pulley 4A of the continuously variable transmission mechanism 4 by spline fitting, the primary pulley 4A is also input. The shaft 7 rotates in the direction opposite to the rotation direction.

  As a result, the reverse drive force is transmitted from the continuously variable transmission mechanism 4 to the wheels (not shown) via the differential 5.

  By the way, in the vehicle transmission 1 described above, oil supplied from an oil pump (not shown) installed therein is supplied to an oil supply path 21 a provided in the sun gear 21 of the planetary gear mechanism 20. The oil in the oil supply passage 21a is blown outward in the radial direction by the rotational centrifugal force of the sun gear 21, and as shown by the thick arrows in FIG. 7, the contact portions of the components of the planetary gear mechanism 20 and the reverse brake Forty-five friction plates 41 and 42 are supplied. Such an oil supply mode is called a centrifugal oil supply system.

  The oil supply passage 21a of the sun gear 21 is a shaft hole provided along the central axis in a region from the rear end surface on the downstream side in the power transmission direction in the side gear 21 to the middle in the axial direction toward the upstream side. Discharge ports 21b... For discharging oil radially outward are provided at several circumferential positions at a plurality of positions in the longitudinal direction of the oil supply passage 21a.

  Here, the part to which the features of the present invention are applied will be described in detail.

  In short, in the forward / reverse switching device 3, the oil supply path for centrifugally supplying oil from the oil supply path 21a provided in the sun gear 21 of the planetary gear mechanism 20 to the reverse brake 40 side is devised.

  First, the ring gear 22 of the planetary gear mechanism 20 is formed as a cylindrical thick member, and the inner diameter side friction plate 31 of the reverse brake 40 is integrally attached to the outer periphery thereof by spline fitting. A positioning plate 26 for positioning the ring gear 22 in the axial direction is attached to one side surface.

  Then, one side surface of the ring gear 22 and the positioning plate 26 are separated in the axial direction to make the separation gap an oil supply passage 50 composed of an annular gap continuous in the circumferential direction, and at several places on the circumference of the ring gear 22. A passage 22b is provided for guiding the oil discharged from the oil supply passage 21a of the sun gear 21 and centrifugally supplied to the oil supply passage 50 to the reverse brake 40 side on the outer diameter side of the ring gear 22.

  Specifically, in the planetary gear mechanism 20 described above, the ring gear 22 is pivoted by the thrust force generated by the rotation of the ring gear 22 because the meshing portions of the gears 21 to 24 are helical teeth. May slide in the direction. In order to regulate and position such an axial slide of the ring gear 22, a positioning plate 26 that integrally covers the inner hole is attached to one side of the ring gear 22. The inner diameter side of the outer surface is brought into contact with the end face of the cylindrical boss portion of the fixed sheave 4A1 of the primary pulley 4A of the continuously variable transmission mechanism 4 via a metal 28 such as a slide bearing, and the inner diameter of the inner surface of the positioning plate 26 A configuration is adopted in which the side is brought into contact with the outer surface of the radially outward flange 25d of the carrier 25 via a thrust roller bearing 27.

  Specifically, the positioning plate 26 is an annular plate that is manufactured by, for example, pressing a metal plate, but has a stepped shape in three stages in the axial direction as shown in FIG.

  The positioning plate 26 has its outer peripheral edge fitted to the inner periphery of the flange 22c provided on the outer peripheral side of the one side surface of the ring gear 22 so as to crush several circumferential portions of the fitting portion. It is integrally attached to the ring gear 22 by caulking.

  In the state where the positioning plate 26 is attached to the ring gear 22, as shown in FIGS. 6 and 7, the outer diameter side region 26 a of the positioning plate 26 has an appropriate outer diameter side annular shape on one side surface of the ring gear 22. The radial direction intermediate region 26b of the positioning plate 26 is opposed to the axial direction non-contact so as to secure the gap 51, and the outer side surface of the radial outward flange 25d of the carrier 25 is interposed through an appropriate intermediate annular gap 52. Opposed in the axial direction, the inner diameter side region 26c of the positioning plate 26 is opposed to the outer surface of the radially outward flange 25d of the carrier 25 in the axial direction via an appropriate inner diameter side annular gap 53.

  These three annular gaps 51 to 53 are continuous in the radial direction, and they constitute a part of the oil supply passage 50 described above.

  A thrust roller bearing 27 is interposed in an inner diameter side annular gap 53 between the inner diameter side region 26c of the positioning plate 26 and the radially outward flange 25d of the carrier 25. The oil passes through from the inner diameter side to the outer diameter side. Further, convex portions 26d for positioning the thrust roller bearing 26 in the radial direction are provided at several places on the circumference of the inner diameter side region 26c of the positioning plate.

  The passage 22b of the ring gear 22 is provided at several places on the circumference of the ring gear 22, and each passage 22b is formed as an oblique hole penetrating from one side surface of the ring gear 22 toward the outer peripheral surface. Yes.

  Further, as shown in FIG. 8, the opening on the outer peripheral surface side of each passage 22b of the ring gear 22 described above is disposed in a missing tooth portion 22d without spline teeth at several circumferential positions on the outer diameter side spline 22a of the ring gear 22. Further, the side surface side opening in each passage 22 b is opened to the outer diameter side annular gap 51 of the oil supply passage 50.

  In addition, the toothless portion 22d of the outer diameter side spline 22a of the ring gear 22 is provided at equal circumferential intervals in consideration of the weight balance of the ring gear 22, but the passage 22b is formed in all the toothless portions 22d. Only the necessary number is provided without providing.

According to such a configuration, the oil supplied to the oil supply path 21a of the sun gear 21 is discharged radially outward from each discharge port 21b by the centrifugal force accompanying the rotation of the sun gear 21 itself. this oil, for example, the sun gear 21 and the thrust roller bearing 12 interposed between the radially outward flange 25 d of the thrust roller bearing 11 and the sun gear 21 and the carrier 25 which is interposed between the input shaft 7 Is supplied to the pinion gears 23 and 24 side, the forward clutch 30 side, and the like.

And the oil discharged from the discharge port 21b on the most downstream side in the oil supply passage 21a of the sun gear 21 is opposed not only to the thrust roller bearing 12 side described above but also to the radial direction between the sun gear 21 and the central shaft portion 25a of the carrier 25. It moves toward the fixed sheave 4A1 side of the primary pulley 4A of the continuously variable transmission mechanism 4 from the gap, passes through the spline fitting portion between the fixed sheave 4A1 and the central shaft portion 25a of the carrier 25, and the radial direction of the carrier 25 The thrust roller bearing 27 interposed between the outward flange 25d and the positioning plate 26 is passed, and the oil supply passage 50 is further reached.

  Here, when the oil reaches the outer diameter side annular gap 51 in the oil supply passage 50, the oil flows into the passage 22 b of the ring gear 22, and the inner diameter side friction plate 41 and the outer diameter side friction plate 42 of the reverse brake 40. Will be led to the site where there is.

  Here, since the side surface side opening in each passage 22 b is opened to the outer diameter side annular gap 51 of the oil supply passage 50, the oil that has reached the outer diameter side annular gap 51 becomes circumferential with the rotation of the carrier 25. Although the oil flows in the direction, since the outer diameter side annular gap 51 is continuous in the circumferential direction, the oil existing in the outer diameter side annular gap 51 easily flows into the side surface side opening of the passage 22b. Become.

  Moreover, since the passage 22b of the ring gear 22 is formed as an oblique hole, both the side surface opening and the outer peripheral surface side opening have an elliptical shape, so that the opening area is larger than a circular hole penetrating in the radial direction as in the conventional example. It can be said that the oil inflow efficiency and the oil discharge efficiency are improved.

  For this reason, the oil centrifugally supplied from the oil supply passage 21a of the sun gear 21 to the oil supply passage 50 can be efficiently guided to the reverse brake 40 side, so that the friction plates 41 and 42 in the reverse brake 40 are provided. It is possible to contribute to improvement of mutual wear resistance and long-term stabilization of the brake performance of the reverse brake 40.

  As described above, in the embodiment to which the present invention is applied, the following operations and effects can be obtained.

  First, the ring gear 22 is formed as a thick cylindrical member, and the inner diameter side friction plate 41 of the reverse brake 40 is spline fitted to the outer diameter side spline 22a. 26, by attaching the ring gear to the positioning member to which the inner diameter friction plate of the reverse brake is attached, as in the conventional example, and then retaining with a snap ring, as in the conventional example, The number of parts and the number of assembling steps can be reduced, and the manufacturing cost can be reduced.

  In addition, in connection with the ring gear 22 being a thick cylindrical member, it is possible to provide an oil passage 22b formed of an oblique hole in the ring gear 22 and the circumferential direction between the ring gear 22 and the positioning plate 26. It is possible to provide an outer-diameter-side annular gap 51 that is continuous with the outer diameter side, and as described above, it is possible to increase the oil supply efficiency to the reverse brake 40 side disposed on the outer-diameter side of the planetary gear mechanism 20. It was.

  Hereinafter, other embodiments of the present invention will be described.

  (1) In the above embodiment, the planetary gear mechanism 20 according to the present invention is used as the forward / reverse switching device 3 of the vehicle transmission 1. However, the planetary gear mechanism 20 according to the present invention includes a ring gear 22. As long as it is used in such a form that the multi-plate frictional engagement device (40) is arranged on the outer diameter side, the use target is not particularly limited.

  (2) In the above embodiment, the double pinion type is exemplified as the planetary gear mechanism 20 according to the present invention, but the configuration thereof is not particularly limited, such as a single pinion type or a ravinio type.

It is a conceptual diagram which shows one Embodiment of the transmission for vehicles used as the application object of the planetary gear mechanism which concerns on this invention. It is the schematic diagram which looked at the longitudinal cross-section of the forward / reverse switching device of FIG. It is the schematic diagram which looked at the forward / reverse switching device of FIG. 1 from the front side of the input side of rotational power, and is a figure used for operation | movement description of the forward / backward switching device at the time of vehicle advance. It is the schematic diagram which looked at the longitudinal cross-section of the forward / reverse switching device of FIG. It is the schematic diagram which looked at the forward / reverse switching device of FIG. 1 from the front side of the rotational power input side, and is a diagram used for explaining the operation of the forward / backward switching device when the vehicle is traveling backward. It is a vertical side view which shows the forward / backward switching apparatus of FIG. 1 in detail. It is the figure which expanded a part of FIG. 6, and has shown the oil supply path | route in detail. It is a perspective view which isolate | separates and shows the ring gear and positioning plate of FIG. FIG. 7 is a view corresponding to FIG. 6 of a conventional forward / reverse switching device. It is the figure which expanded a part of FIG. 9, and has shown the oil supply path | route in detail. It is a perspective view which shows the ring gear of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Vehicle transmission 2 Fluid coupling 3 Forward / reverse switching device 4 Continuously variable transmission mechanism 5 Differential 6 Transmission case 7 Input shaft 20 Planetary gear mechanism of forward / reverse switching device 21 Sun gear of planetary gear mechanism 21a Sun gear oil supply path 22 Planet Ring gear 22a of the gear mechanism Outer diameter side spline 22b of the ring gear 22b Passage 22c of the ring gear 23 Cage of the ring gear 23 Inner diameter side pinion gear 24 of the planetary gear mechanism 24 Outer diameter side pinion gear 25 of the planetary gear mechanism 25 Carrier 25a of the planetary gear mechanism Carrier center shaft portion 25c Carrier annular plate 25d Carrier radial outward flange 26 Positioning plate 27 Thrust roller bearing 30 Forward clutch of forward / reverse switching device 40 Reverse brake of forward / reverse switching device (multiplate friction engagement of claims) apparatus)
41 Reverse Brake Inner Diameter Friction Plate 42 Reverse Brake Outer Diameter Friction Plate 43 Reverse Brake Actuator 50 Oil Supply Path 51 Outer Diameter Side Annular Gap 52 Containing Oil Supply Path 52 Intermediate Ring Gap Containing Oil Supply Path 53 Construct Oil Supply Path Inner ring gap

Claims (2)

An oil supply path provided in the sun gear and provided with a multi-plate friction engagement device for switching between a free state in which the ring gear can rotate and a locked state in which the ring gear cannot be rotated on the outer diameter side of the ring gear A planetary gear mechanism that employs a centrifugal oil supply system that supplies oil discharged from the sun gear to the multi-plate frictional engagement device side by the rotational centrifugal force of the sun gear,
The ring gear is a cylindrical thick member to which an inner diameter side friction plate of the multi-plate friction engagement device is integrally attached to an outer periphery thereof,
A positioning plate for positioning the ring gear in the axial direction is attached to one side surface of the ring gear. The one side surface of the ring gear and the positioning plate are separated from each other in the axial direction, and the separation gap is circumferentially arranged. An annular gap that continues to
The ring gear is provided with a passage for guiding oil discharged from the oil supply passage of the sun gear and centrifugally supplied to the annular gap to the multi-plate friction engagement device side,
The passage is an oblique hole that opens to the side surface and the outer diameter side of the ring gear,
The ring gear and the inner diameter side friction plate are coupled to each other via a spline so as to be integrally rotatable, and at least one spline tooth in the outer diameter side spline of the ring gear is eliminated. Side openings are arranged,
An inner surface of the positioning plate is brought into contact with an outer surface of a radially outward flange provided in a carrier that supports a plurality of pinion gears via a thrust roller bearing, so that the positioning plate and the carrier are radially outside. The axially facing gap with the directional flange is a relay path that guides oil from the oil supply path to the annular space,
The center shaft portion of the carrier is hollow, and the center shaft portion is fitted on one end side of the sun gear in a relatively rotatable state, and the discharge port of the oil supply path is disposed on one end side of the sun gear. Accordingly, the radially opposed gap between the center shaft portion of the carrier and the sun gear and the discharge port are the upstream portion of the oil supply path when the oil is guided from the oil supply path to the annular space. A planetary gear mechanism. A vehicular transmission having a forward / reverse switching device that switches a rotational power input from an internal combustion engine as necessary to a vehicle forward state in which the rotational power is output in the same rotational direction or a vehicle reverse state in which the rotational power is reversed and output in the reverse rotational direction. There,
The forward / reverse switching device includes the planetary gear mechanism according to claim 1, a forward multi-plate friction engagement device, and a reverse multi-plate friction engagement device.
In the planetary gear mechanism, the sun gear is used as an input shaft for rotational power from the internal combustion engine, and the center shaft portion of the carrier is used as an output shaft.
Further, the forward multi-plate friction engagement device includes an inner diameter side friction plate that is integrally attached to a carrier outer diameter side of the planetary gear mechanism, and an inner diameter of a member that is rotatably attached to the sun gear of the planetary gear mechanism. An outer diameter friction plate that is integrally attached to the side, and an actuator that switches the carrier to a free state that allows relative rotation with respect to the sun gear or a locked state that enables integral rotation.
The reverse multi-plate friction engagement device includes an inner diameter side friction plate integrally attached to an outer diameter side of the ring gear of the planetary gear mechanism, an outer diameter side friction plate integrally attached to a transmission case, A vehicle transmission comprising: an actuator that switches the ring gear to a free state in which the ring gear can rotate or a locked state in which the ring gear cannot rotate .

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