JPH0514044Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Field of Industrial Application) The present invention is directed to a clutch drum which is spline-coupled to one of a pair of rotating shafts as a power transmission shaft and is brought into sliding contact with the other rotating shaft. The present invention relates to a clutch device for an automatic transmission equipped with a clutch device.

(Prior Art) A known example of this type of clutch device is the one disclosed in Japanese Utility Model Publication No. 56-26123.

However, in this known example, the clutch drum, which is spline-coupled to the turbine shaft, is centered by fitting a spline joint that has play in the radial direction due to its structure. The centering of the drum was uncertain, and in some cases there was a risk that the performance of the clutch system would be degraded.

Further, in this known example, two seal rings used for sealing the relative sliding parts are arranged at an appropriate interval in the axial direction on the outer surface of the rotating shaft that makes sliding contact with the clutch drum, and the pair of seal rings are arranged at appropriate intervals in the axial direction. The ring ensures sealing between the drum-side oil passage formed on the clutch drum side and the shaft-side oil passage formed on the rotating shaft side so as to communicate with the drum-side oil passage. However, in this case, the seal ring is more expensive than a sealing material with a simple structure such as an O-ring used for sealing a fixed fitting part, and moreover, it requires an oil passage inside the hollow rotating shaft. The problem is that the process is relatively difficult because of the formed structure, which tends to increase costs.

On the other hand, as a method for improving the problems in the above-mentioned known example (publication of Utility Model Publication No. 56-26123), for example, Japanese Patent Application Laid-Open No. 131450/1983 discloses that a hollow rotating shaft is disposed outside one rotating shaft. In addition, in a structure in which a clutch drum is fitted into the hollow rotating shaft and the clutch drum is spline-coupled to the hollow rotating shaft, when forming an oil passage for supplying hydraulic pressure to the clutch drum side, the inside of the hollow rotating shaft is By arranging a cylindrical member on the circumferential side and forming an oil passage extending in the axial direction between the cylindrical member and the hollow rotating shaft, it is possible to form an oil passage directly inside the hollow rotating shaft. Furthermore, by bringing the outer peripheral surface of the hollow rotating shaft into contact with the inner peripheral surface of the clutch drum in a non-rotating state, the centering performance of the clutch drum is improved, and a pair of O-rings are inserted between the two. Disclosed is a device in which a seal is arranged to ensure sealing performance at the portion.

However, although this known example has the advantage that both the pair of seal members can be constructed from inexpensive O-rings, it does not require the use of a cylindrical member, a separate member that is unnecessary in the original structure of an automatic transmission. Since it forms a path, there are problems in that the number of parts increases and the structure becomes complicated, so even if the above-mentioned advantages are taken into account, it is difficult to say that it is necessarily a suitable configuration.

(Purpose of the invention) The present invention attempts to solve or improve the problems pointed out in the above-mentioned section of the prior art. In a clutch device for an automatic transmission having a clutch drum that is slidably fitted to the other rotating shaft, the clutch drum is easily and reliably centered, and is an essential component of an automatic transmission without providing a separate member. The purpose of this invention is to form an oil passage by using members more effectively, thereby simplifying the structure and reducing the cost.

(Means for Achieving the Objects) The present invention provides the following as means for achieving the above objects:
a convex portion is formed on the spline side of the rotating shaft, and the convex top surface is brought into contact with the inner circumferential surface of the clutch drum; (2) arranged on the first rotating shaft and the outer periphery of the first rotating shaft; A first oil passage is formed between the clutch drum and the hollow second rotating shaft.
forming a second oil passage communicating with the oil passage; (3) forming a step-down surface on the inner circumferential surface of the clutch drum that is lower than a surface that abuts the top surface of the convex portion of the first rotating shaft; (4) the convex portion of the first rotating shaft; An O-ring is disposed on the outer surface of the end of the second rotating shaft, and a seal ring is disposed on the outer surface of the end of the second rotating shaft. The second oil passage is opened.

(Function) In the present invention, (1) By means (1) above, the top surface of the convex part of the first rotating shaft and the inner circumferential surface of the clutch drum, which are abuttingly fitted to each other, can be used to connect the clutch drum. (2) By means (2) above, it is not necessary to form an oil passage inside the second rotating shaft, and the oil passage can be easily formed. , (3) By means (3) and (4) above, one of the seals is constructed as one of the pair of seals located on both sides of the connecting portion of the first oil passage and the second oil passage in the axial direction. It is possible to use an O-ring which is simple and inexpensive.

(Embodiment) Hereinafter, a preferred embodiment of the present invention will be described with reference to FIGS. 1 and 2.

First, the overall structure of an automatic transmission equipped with a clutch device according to an embodiment of the present invention (in this embodiment, the fourth clutch device described later corresponds to this) will be explained. This automatic transmission is shown in FIG. Like,
A torque converter 2 and a multi-speed gear device 3 are arranged coaxially with a crankshaft 1 of an engine (not shown) in order from the engine side.

The torque converter 2 includes a pump 4, a turbine 5, and a stator 6. Pump 4 is fixed to crankshaft 1. The stator 6 is
It rotates on a fixed shaft 9 which is integrated with the transmission case 8 via a one-way clutch device 7. The one-way clutch device 7 allows the stator 6 to rotate in the same direction as the pump 4,
This functions to restrict rotation in the opposite direction.

The multi-speed gear device 3 has a central shaft 11 that passes through the center of the multi-speed gear device 3 in its axial direction.
It is equipped with The central shaft 11 has one end connected to the crankshaft 1, and the other end extends to the side wall 30 of the multi-speed gear unit 3 through the center thereof, and an oil pump is disposed on the side wall 30. It is connected to 10. A hollow long-shaft turbine shaft 12 is disposed on the outside of the central shaft 11 so as to overlap the central shaft 11 in the radial direction over almost its entire axial length. This turbine shaft 12 corresponds to a first rotating shaft as defined in the claims of the utility model registration, and as shown in enlarged views in FIGS. 1 and 2, its base end 12a is connected to the torque converter 2.
is connected to the turbine 5, and its tip 12b
is connected to the side wall 30.

On the other hand, a Ravigneau type planetary gear unit 13 is provided on the turbine shaft 12.
The planetary gear unit 13 includes a small diameter sun gear 14, a large diameter sun gear 15 disposed on the side of the small diameter sun gear 14 far from the engine, a long pinion gear 16, a short pinion gear 17, and a ring gear 18. On the side of the planetary gear unit 13 far from the engine are first and second clutch devices 19, 20.
are arranged in parallel. The first clutch device 1
Reference numeral 9 serves to connect and disconnect power transmission between the small diameter sun gear 14 and the turbine shaft 12 via the first one-way clutch device 21. On the other hand, the second
The clutch device 20 includes the first clutch device 19
The small diameter sun gear 14 and the turbine shaft 12 are parallel to each other.
It is used to interrupt power transmission between the A first brake device 22 is arranged radially outward of the second clutch device. The first brake device 22 is a band brake, and includes a brake drum 22a connected to the large diameter sun gear 15 and a brake band 22b hooked onto the brake drum 22a. A third clutch device 23 is disposed radially outward of the second clutch device 20 and on the side of the first brake device 22.
is located. The third clutch device 23 is
Brake drum 22 of the first brake device 22
The large diameter sun gear 15 and the turbine shaft 1 are connected to each other via a.
This is used to connect and disconnect power transmission between the two.

A second brake device 24 is disposed radially outward of the planetary gear unit 13 for engaging and disengaging the carrier 13a of the planetary gear unit 13 and the transmission case 8 of the multi-speed gear device 3. A second one-way clutch device 25 is disposed between the first brake device 22 and the second brake device 24 in parallel with the second brake device 24 for engaging and disengaging the carrier 13a and the transmission case 8. There is.

A fourth clutch device 26 according to an embodiment of the present invention is disposed on the side of the planetary gear unit 13 on the engine side. . An output gear 27 connected to the ring gear 18 is disposed on the side of the fourth clutch device 26 on the engine side. The output from the output gear 27 is transmitted to a drive shaft (not shown) via an idle gear 28 and a differential ring gear 29. This output gear 27 corresponds to the second rotating shaft as defined in the claims of the utility model registration.

This embodiment is directed to an assembly structure between the fourth clutch device 26, the turbine shaft 12, and the output gear 27, and this assembly structure will be described in detail below.

The fourth clutch device 26 includes a clutch drum 3 which is formed by integrally joining a first piece 32A which becomes a boss part and a second piece 32B made of steel plate which becomes a drum part.
It has 2. This clutch drum 32 divides the inner circumferential surface of the first piece 32A into approximately three equal parts in the axial direction, and divides these into three parts from the anti-engine side, a spline 34 and a smooth fitting surface 37 (this fitting surface 37 is a utility model). (corresponding to the inner circumferential surface in the scope of the registered claims) and a stepped surface 38 that is stepped down from the fitting surface 37 (in other words, has a larger diameter than the fitting surface 37). This clutch drum 32 is
The spline 34 is meshed with a spline 35 formed on the turbine shaft 12, and the fitting surface 37 formed on the side of the spline 34
is attached to the turbine shaft 12 in a state in which it is fitted in contact with the top surface 36a of a convex portion 36 formed on the side of the spline 35 of the turbine shaft 12. In this case, the centering of the clutch drum 32 with respect to the turbine shaft 12 is not done by the spline portion with fitting play in the radial direction, but by the fitting surface 37 of the clutch drum 32 and the convex portion 36 of the turbine shaft 12 that are closely fitted to each other. Since the clutch drum 32 is centered by fitting the spline portion, the centering accuracy is higher than that in the case where the clutch drum 32 is centered by fitting the spline portion, and more advanced and reliable centering is realized. Consequently, the operating performance of the fourth clutch device 26 is further improved.

On the other hand, the output gear 27 fitted onto the outer periphery of the turbine shaft 12 is supported by a bearing 31 fitted between the turbine shaft 12 so as to be rotatable relative to the turbine shaft 12. , between the inner peripheral surface and the outer peripheral surface of the turbine shaft 12,
A first oil passage 41 is formed that extends in the axial direction and opens on the end 27a side of the output gear 27 on the fourth clutch device 26 side. The output gear 27 is attached with its end 27a inserted into the step-down surface 38 of the clutch drum 32, and its end outer surface 27b is brought into sliding contact with the step-down surface 38. . Further, the first oil passage 41, which opens toward the end 27a of the output gear 27, is connected to a step-down surface 38 of the clutch drum 32 outside the end 27a, and an actuator formed inside the clutch drum 32. The clutch drum 32 is in communication with the oil chamber 33.
The first piece 32A is communicated with a second oil passage 42 provided through the first piece 32A in the radial direction, and the hydraulic oil supplied through the first oil passage 41 is operated through the second oil passage 42. It is introduced into the oil chamber 33.

The sealing performance of the first oil passage 41 and the second oil passage 42 is determined by the outer end surface 2 of the output gear 27.
The end outer surface 2 is sealed with a seal ring 43 provided on 7b.
7b and the step-down surface 38 of the clutch drum 32, and an O-ring 44 provided on the top surface 36a of the convex portion of the turbine shaft 12 seals the top surface 36a of the convex portion and the clutch drum 32. Fitting surface 37
This is ensured by sealing the second seal portions 46 in between. In this case, of the two seal parts, only the first seal part 45 is a sliding contact part,
Since the second seal part 46 is a non-sliding contact part, a relatively expensive seal ring can be attached only to the first seal part 45, and an inexpensive O-ring can be used for the second seal part 46. The manufacturing cost is lower than in the case where the two seal parts are both sliding contact parts and expensive seal rings must be used for each of the two seal parts.

In this case, the above-mentioned publicly known example (Unexamined Japanese Patent Publication No.
58-131450), but in this embodiment, the first oil passage 41 can be constructed as an existing component that is essential for the function of the automatic transmission without providing any separate component. Since it can be formed by using a sealant, the number of parts is reduced and the structure can be simplified, which more than offsets the drawback of increased cost of the sealant. It can be said that this structure produces useful effects and has a higher technical effect.

Further, the first oil passage 41 communicating with the second oil passage 42 of the clutch drum 32 is connected to the turbine shaft 12 and the output gear 2 disposed on the outer periphery of the turbine shaft 12.
7, the oil passage can be formed more easily than in the case where the oil passage is formed penetrating inside the output gear 27 as shown in, for example, Japanese Utility Model Publication No. 56-26123. It also has the advantage that it can be formed at low cost.

(Effects of the invention) As is clear from the above description, the clutch device of the automatic transmission of the invention has the following features: (1) centering of the first rotating shaft and the clutch drum spline-coupled to the first rotating shaft; This is achieved by bringing the top surface of the convex portion formed on the side of the spline of the first rotating shaft into contact with the inner circumferential surface of the clutch drum.
Conventional clutch devices (for example, Utility Model 56-
(2) Centering is easier and more reliable than in the case where the first rotating shaft and the clutch drum are centered by fitting a spline part as in the case of 26123 Publication). Utility Model Publication No. 56-26123 because the second oil passage communicating with the first oil passage formed is constituted by a fitting gap formed between the first rotating shaft and the second rotating shaft. The clutch device shown in Fig. 1 forms an oil passage inside the second rotating shaft, or the clutch device shown in JP-A-58-131450, which forms an oil passage with a separate member. (3) Of the pair of seal parts that seal the oil passage, one is a sliding seal part and the other is a non-sliding seal part. It is possible to use a relatively expensive seal ring only for the sliding seal part and use an inexpensive O-ring for the other non-sliding seal part. In this way, manufacturing costs can be lowered compared to the case where expensive seal rings are attached to both seal parts, and both seal parts can be attached to O While it is possible to seal with a ring, it has the following effects: it can reduce the manufacturing cost from a comprehensive perspective and simplify the structure compared to the case where a separate member is required for forming the oil passage. can get.

[Brief explanation of the drawing]

1 is an enlarged view of a portion of FIG. 2, and FIG. 2 is a cross-sectional view of an automatic transmission equipped with a clutch device according to an embodiment of the present invention. 1...Crankshaft, 2...Torque converter,
3... Multi-speed gear device, 12... First rotating shaft (turbine shaft), 13... Planetary gear unit, 24... Clutch device, 27... Second rotating shaft (output gear), 32... Clutch drum , 36... Convex portion, 37... Inner peripheral surface (fitting surface),
41...First oil passage, 42...Second oil passage, 43...
Seal ring, 44...O ring.

Claims (1)

[Scope of utility model registration request] Spline-coupled to a first rotating shaft serving as a power transmission shaft, and slidingly contacted to a hollow second rotating shaft serving as another power transmitting shaft disposed around the outer periphery of the first rotating shaft. A clutch device for an automatic transmission having a clutch drum, wherein a first oil passage is provided between the first rotating shaft and the second rotating shaft, and the clutch drum is connected to the first oil passage. Further, the clutch drum is centered by the inner peripheral surface on the side of the spline portion coming into contact with the top surface of the convex portion provided on the side of the spline portion of the first rotating shaft. At the same time, the inner circumferential surface of the clutch drum is formed with a step-down surface that is stepped down from the surface that contacts the top surface of the convex portion, and the step-down surface extends in the axial direction within the step-down surface. The second rotary shaft is brought into sliding contact with the outer surface of the extended end of the first rotary shaft, and an O-ring is attached to the protrusion of the first rotary shaft. Seal rings are disposed on the outer surface of each end of the rotating shaft, and the second oil passage is opened on the inner circumferential surface of the clutch drum which is axially sandwiched between the O-ring and the seal ring. A clutch device for an automatic transmission characterized by: