JPH0533809Y2 - - Google Patents

Description

[Detailed explanation of the idea]

(Field of Industrial Application) The present invention relates to a planetary gear device for an automatic transmission installed in an automobile. (Prior Art) In an automatic transmission in which a torque converter is combined with a speed change gear, and a plurality of gears are obtained by switching the power transmission path of the speed change gear through selective operation of a plurality of frictional fastening members. In this case, a planetary gear device is used as the speed change gear device. This planetary gear device generally includes a sun gear, a plurality of pinion gears meshed with the sun gear, a carrier that rotatably supports each of the pinion gears via a pinion gear shaft, and a ring meshed with each pinion gear. In the case of a so-called Lavignillo type planetary gear device, a large sun gear and a small sun gear are arranged in parallel on the same axis, and a plurality of short pinion gears meshed with the small sun gear.
A plurality of long pinion gears meshed with the short pinion gear and the large sun gear, a carrier rotatably supporting the short pinion gear and the long pinion gear via pinion gear shafts, and a plurality of long pinion gears meshed with the long pinion gear. It consists of a ring gear. In an automatic transmission, such a planetary gear device is disposed adjacent to another rotating member on the same axis, and in that case, the planetary gear device and the adjacent rotating member can be smoothly rotated relative to each other. In order to achieve this, an annular thrust bearing is usually provided between the two, as disclosed in, for example, Japanese Unexamined Patent Publication No. 56-156549. As shown in FIG. 7, this thrust bearing has a large number of needles 2 disposed and held in the radial direction on a retainer 1 to form an annular structure as a whole, and the back surface of the retainer 1 is attached to one rotating member 2. The needles 2...2 are arranged so as to face the other rotating member 4 (in this case, the carrier of the planetary gear device). In this case, since the end surface of the carrier in the planetary gear device has a relatively rough surface, if the needles 2...2 are brought into direct contact with the end surface, the needles 2...2 or the thrust bearing will be easily damaged. Needle 2...2
As shown in the figure, an annular bearing race 5 is interposed between the end face 4a and the end face 4a. However, when the back surface 5a of this bearing race 5 rotates relative to the end surface 4a of the carrier 4, the back surface 5
a will wear out early. Therefore, the bearing race 5 is provided with a locking pawl 5b protruding in the axial direction on the peripheral edge, and the locking pawl 5b is attached to the end surface 4.
The bearing race 5 is configured to be prevented from rotating relative to the carrier 4 by engaging with the engagement recess 4b provided in the bearing race 5a. However, with such a configuration, the structure of the carrier in the planetary gear device becomes complicated due to the engagement recess 4b, and the cost increases due to an increase in the number of processing steps. (Purpose of the invention) The present invention deals with the above-mentioned actual situation regarding a planetary gear device of an automatic transmission, and a thrust bearing member is interposed between the planetary gear device and a rotating member adjacent thereto. In a configuration in which a bearing race member is interposed between the bearing member and the planetary gear device, the bearing race member can be prevented from rotating relative to the carrier of the planetary gear device without particularly providing a recess for engagement of a locking pawl. The configuration is as follows. This results in
It is an object of the present invention to prevent wear on the back surface of the bearing race member due to relative rotation of the bearing race member with respect to the carrier, without complicating the structure or increasing the number of processing steps due to the provision of the engagement recess. (Structure of the invention) That is, the planetary gear device for an automatic transmission according to the invention includes a sun gear, a pinion gear, a carrier that rotatably supports the pinion gear via a pinion gear shaft, and a ring gear. In the planetary gear device, both ends of the pinion gear shaft are fitted into holes drilled in the carrier and fixed by caulking, and a bearing race member is inserted from the carrier side between the carrier and the rotating member adjacent thereto. When a thrust bearing member is installed, the end face of the pinion gear shaft is caulked so as not to protrude from the end face of the carrier, and the locking pawl provided on the outer peripheral edge of the bearing race member is crimped to prevent the end face of the pinion gear shaft from protruding from the end face of the carrier. It is configured to engage with a recess in the end face.
This recess is a caulking recess provided in advance on the end face of the pinion gear shaft to facilitate caulking the end of the pinion gear shaft to the carrier, or a recess formed on the end face by caulking,
In either case, since the locking pawl of the bearing race member is engaged with this recess, there is no need to provide a separate recess for engaging the locking pawl on the carrier, and in particular, the end face of the pinion gear shaft is Since the bearing race member is caulked so as not to protrude from the end surface, the bearing race member, whose locking pawl is engaged with the recessed portion of the end surface of the shaft, is well held without coming up from the end surface of the carrier. (Effect of the invention) According to the above configuration, when the bearing race member is disposed in opposition to the carrier of the planetary gear device, the bearing race member is prevented from rotating with respect to the carrier. Abrasion of the back surface of the race member due to sliding of the race member against a carrier having a large surface roughness is prevented. In particular, since the bearing race member is prevented from rotating by using the caulking recess on the end surface of the pinion gear shaft in the planetary gear device or the recess created by caulking, it is necessary to separately provide a rotation-preventing recess in the carrier. disappears. This simplifies the structure of this type of planetary gear device, reduces the number of processing steps, and reduces costs. (Example) Hereinafter, an example of the present invention will be described. First, the outline and operation of an example of an automatic transmission to which the present invention is applied will be explained. As shown in FIG. 1, this automatic transmission 10 includes:
As a main component, a torque converter 20
, a Ravigneaux-type planetary gear device 30 , and a plurality of clutches and brakes for switching the power transmission path of the gear device 30 . The torque converter 20 includes a pump 22 fixedly installed in a case 21 connected to the engine output shaft 11, and a turbine 23 disposed opposite to the pump 22 and driven by the pump 22 via fluid. , a stator 25 which is interposed between the pump 22 and the turbine 23 and supported by the transmission case 12 via a one-way clutch 24 to increase torque; and the case 21 and the turbine 2.
3 and directly connects the engine output shaft 11 and the turbine 23 via the case 21. The rotation of the turbine 23 is input to the planetary gear device 30 via the turbine shaft 27. Here, a pump shaft 13 passing through a turbine shaft 27 is connected to the engine output shaft 11, and the shaft 1
3, an oil pump 14 provided at the rear end of the transmission is driven. On the other hand, the planetary gear device 30 has a small diameter small sun gear 3 loosely fitted on the turbine shaft 27, as shown in FIG. 1 and FIGS. 3 and 4.
1, a large diameter sun gear 32 loosely fitted on the turbine shaft 27 behind the sun gear 31, and a plurality of short pinion gears 33 meshed with the small sun gear 31.
A long pinion gear 34 whose front half is meshed with the short pinion gear 33 and whose rear half is meshed with the large sun gear 32, and a carrier 35 which rotatably supports the long pinion gear 34 and the short pinion gear 33. and a ring gear 36 meshed with the front half of the long pinion gear 34.
It is made up of. As shown in FIG. 1, a forward clutch 41 and a first one-way clutch 42 are interposed in series between the turbine shaft 27 and the small sun gear 31, and a forward clutch 41 and a first one-way clutch 42 are interposed in parallel with these clutches 41 and 42. A coasting clutch 43 is interposed between the turbine shaft 27 and the carrier 35.
A four clutch 44 is interposed, and a reverse clutch 45 is further interposed between the turbine shaft 27 and the large sun gear 32. Further, a 2-4 brake 46 for fixing the large sun gear 32 is provided between the large sun gear 32 and the reverse clutch 45, and a 2-4 brake 46 is provided between the large sun gear 32 and the reverse clutch 45.
The carrier 35 is disposed between the transmission case 12 and the transmission case 12.
2nd one-way clutch 47 that absorbs the reaction force of
and a low reverse brake 48 for fixing the carrier 35 are provided in parallel. The ring gear 36 is connected to an output gear 50, and the left and right axles 50 are connected to the output gear 50 via a differential device 51.
2 and 52 (see Fig. 2). Next, each of the above-mentioned clutches and brakes 41 to 48
To explain the relationship between the operating state and the gear position, first, in 1st gear, the forward clutch 41 is engaged and the first and second one-way clutches 42, 47 are engaged.
becomes locked. Therefore, the output rotation of the torque converter 20 is input from the turbine shaft 27 to the small sun gear 31 of the planetary gear device 30 via the forward clutch 41 and the first one-way clutch 42. In this case, by the action of the second one-way clutch 47, the carrier 35
is fixed, the planetary gear device 30 is
It operates as a fixed gear train without differential operation that transmits rotation from the small sun gear 31 to the ring gear 36 via the short pinion gear 33 and long pinion gear 34. As a result, a first speed state with a large reduction ratio corresponding to the ratio of the diameters of the small sun gear 31 and the ring gear 36 is obtained. Here, since the second one-way clutch 47 idles during coasting, the low reverse brake 48 parallel to the second one-way clutch 47 is engaged in the first range for operating the engine brake. Next, in second gear, in addition to the first gear state (the low reverse brake 48 is released), the 2-4 brake 46 is activated, and the large sun gear 32 in the planetary gear device 30 is fixed. , the second one-way clutch 47 becomes idle. Therefore, the turbine shaft 2
7 to the small sun gear 31 is transmitted to the long pinion gear 34 via the short pinion gear 33.
When the long pinion gear 3 rotates, the large sun gear 32 that meshes with it is fixed.
4 revolves on the large sun gear 32, and the carrier 35 rotates accordingly. As a result, the rotation of the ring gear 36 is increased by the rotation amount of the carrier 35 (revolution of the long pinion gear 34) compared to the 1st speed state, and a 2nd speed state with a smaller reduction ratio than in the 1st speed state is obtained. It will be done. Furthermore, in 3rd gear, the 2-4 brake 46 is released from the 2nd gear state, and the 3-4 brake 46 is released from the 2nd gear state.
Clutch 44 is engaged. Therefore, the rotation of the turbine shaft 27 is simultaneously input to the small sun gear 31 via the forward clutch 41 and the first one-way clutch 42,
It will also be input to the carrier 35 via the clutch 44. As a result, the planetary gear device 3
A third speed state is obtained in which the entire gear 0 rotates integrally and the ring gear 36 rotates at the same speed as the turbine shaft 27. Further, in the fourth speed, the forward clutch 41 is released from the third speed state, and the 2-4 brake 46 is re-engaged. Therefore, the rotation of the turbine shaft 27 is transmitted from the 3-4 clutch 44 to the carrier 3 of the planetary gear device 30.
5, and the long pinion gear 34 is rotated. However, since the large sun gear 32 with which the long pinion gear 34 is engaged is fixed by the 2-4 brake 46, the long pinion gear 34 is It will rotate while revolving together with the carrier 35. As a result, the ring gear 36 that meshes with the long pinion gear 34 is connected to the carrier 3.
5 rotation (rotation of the turbine shaft 27), the rotation speed is increased by the amount of rotation of the long pinion gear 34, thereby obtaining the 4th speed in an overdrive state. Furthermore, at reverse speed, the reverse clutch 4
5 and the low reverse brake 48 are engaged, and the rotation of the turbine shaft 27 is input to the large sun gear 32 of the planetary gear device 30.
The carrier 35 of the gear device 30 is fixed. Therefore, rotation is transmitted through a fixed gear train from the large sun gear 32 to the ring gear 36 via the long pinion 34, and the rotation is transmitted through a fixed gear train that corresponds to the ratio of the diameters of the large sun gear 34 and the ring gear 36. A reduction ratio is obtained, but in this case the direction of rotation of the ring gear 36 is opposite to the direction of rotation of the turbine shaft 27 or large sun gear 32. The first one-way clutch 42, which transmits rotation during the first to third speeds, will idle during coasting, but in this case, the coasting clutch 43 is engaged instead of the first one-way clutch 42. Table 1 summarizes the relationship between the above-mentioned clutch and brake operations and gear positions.

【table】

[Table] Next, the peripheral structure of the planetary gear device 30, which is a characteristic part of the present invention, will be described in more detail. As shown in FIGS. 3 and 4, this planetary gear device 30 includes a small sun gear 31, a large sun gear 32, a short pinion gear 33, a long pinion gear 34, and a carrier 3.
In the illustrated example, three short pinion gears 33 and three long pinion gears 34 are provided between the front member 35a and the rear member 35b of the carrier 35. It is rotatably supported by a short pinion gear shaft 37 and a long pinion gear shaft 38, which are installed one by one. Both ends of each of the pinion gear shafts 37 and 38 are fitted into holes drilled in the front and rear members 35a and 35b of the carrier 35, respectively, and the crimping tool A is inserted into the holes as shown in FIG. It is caulked by partially applying an external force to the end face using a screwdriver, thereby fixing it to the carrier 35. In that case, in order to perform this caulking well, caulking recesses 3 are provided at both ends of each pinion gear shaft 37, 38.
7a and 38a are provided in advance, and this caulking is performed so that both ends of the pinion gear shafts 37 and 38 are connected to the front and rear members 35 of the carrier 35.
This is done so that it does not protrude from the end faces 35a', 35b' of a, 35b. On the other hand, in front of this planetary gear device 30 is located a hub 44b that is integrated with the drum 44a of the 3-4 clutch 44 and spline-fitted to the turbine shaft 27, and in the rear of the gear device 30 is a large sun gear 32. and 2-4 above.
A flange portion 46b coupled to the drum 46a of the brake 46 is located, and these hubs 44
b, flange portion 46b, and planetary gear device 3
The front of the carrier 35 at 0, the rear member 35a,
35b, there are first and second thrust bearings 61, 62 and these bearings 61, 62.
First and second bearing races 63 and 64 are interposed in pairs, respectively, to be in contact with the needles. And the first and second bearing races 63,
64 are provided with three locking claws 63a and 64a each that protrude a predetermined amount in the axial direction, and three locking claws 63a and 64a of the first bearing race 63 are provided.
3a are respectively engaged with caulking recesses 37a in the front end surfaces of the pinion gear shafts 37 that pivotally support the short pinion gear 33, and the three locking pawls 64a of the second bearing race 64 hold the long pinion gear 34. Each of the pinion gear shafts 38 is engaged with a caulking recess 38a on the rear end surface of each pinion gear shaft 38 that is pivotally supported. According to the above configuration, the planetary gear device 30
first and second bearing races 63, which are arranged on both sides of the carrier 35, and in which the needles of the first and second thrust bearings 61, 62 are in contact with each other;
64, the locking claws 63a and 64a are connected to the carrier 3.
By being engaged with the caulking recesses 37a, 38a on the end faces of the pinion gear shafts 37, 38 in 5, rotation with respect to the carrier 35 is prevented. In that case, the ends of the pinion gear shafts 37, 38 are connected to the front and rear members 35 of the carrier 35, as shown in FIG.
Since the bearing races 63 and 64 are caulked so as not to protrude from the end surfaces 35a, ′, and 35b′ of the carrier 35, the bearing races 63 and 64 are held well without coming up from the end surfaces of the carrier 35, and are held well. Wear on the back surfaces of the bearing races 63, 64 due to sliding on the end surfaces 35a', 35b' of the front and rear members 35a, 35b of the carrier 35, which have large surface roughness, is prevented. Particularly, according to the above configuration, the bearing race 6 is tightened using the caulking recesses 37a and 38a of the end surfaces of the pinion gear shafts 37 and 38.
3 and 64, there is no need to provide separate anti-rotation recesses in the front and rear members 35a and 35b of the carrier 35. This results in
The structure of the carrier 35 is simplified and the number of manufacturing steps is reduced. Note that the above embodiment is based on the pinion gear shaft 3.
Bearing races 63, 64 are attached to caulking recesses 37a, 38a provided in advance on the end faces of 7, 38.
However, as shown in FIG. 6, the bearing races 63 are fitted into the recesses 37a' and 38a' formed by caulking on the end faces of the pinion gear shafts 37' and 38'. ',6
4' may be engaged with the locking claws 63a' and 64a'. Here, also in this embodiment, the caulking is performed so that the ends of the pinion gear shaft do not protrude from the end surfaces of the front and rear members of the carrier.

[Brief explanation of the drawing]

FIG. 1 is a schematic diagram showing one configuration example of an automatic transmission to which an embodiment of the present invention is applied, FIG. 2 is a partially longitudinal side view of the automatic transmission, and FIG. 3 is a planetary gear in the transmission. Enlarged vertical side view around the device, No. 4
The figures are a front view of the planetary gear device and its surroundings taken along the line of Fig. 3, Fig. 5 is an enlarged sectional view of the main part showing the pinion gear shaft in a swaged state, and Fig. 6 shows another embodiment of the present invention. It is a main part front view. FIG. 7 is a longitudinal sectional side view showing the general configuration of a thrust bearing. 10... Automatic transmission, 30... Planetary gear device, 31, 32... Sun gear, 33, 34...
Pinion gear, 35...Carrier, 35a', 35
b'...End face of carrier, 36...Ring gear, 3
7, 38...Pinion gear shaft, 37a, 3
8a... Recessed portion for caulking, 37a', 38a'... Recessed portion caused by caulking, 61, 62... Thrust bearing member, 63, 64, 63', 64'...
Bearing race member, 63a, 64a, 63
a', 64a'...Latching claw.

Claims (1)

[Scope of utility model registration request] A planetary gear device for an automatic transmission comprising a sun gear, a pinion gear, a carrier rotatably supporting the pinion gear via a pinion gear shaft, and a ring gear, wherein both ends of the pinion gear shaft are connected to the carrier. The carrier is fitted into a hole drilled in the carrier, and is fixed to the carrier by caulking by partially applying force to the end face so that the end face does not protrude from the end face of the carrier. A bearing race member and a thrust bearing member are disposed from the carrier side between the rotary member and the rotating member, and a locking pawl that protrudes a predetermined amount in the axial direction is provided on the outer peripheral edge of the bearing race member. The bearing race member is prevented from rotating relative to the carrier by the retaining pawl being engaged with a caulking recess provided on the end face of the pinion gear shaft or a recess created by caulking. Planetary gear device for automatic transmission.