JP2012137169A - Stationary cylinder type clutch device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a stationary cylinder type clutch device capable of preventing a carrier from being worn out due to the abutment to a pawl piece provided in the outer circumferential portion of the race of a thrust bearing.SOLUTION: The stationary cylinder type clutch device comprises a female involute spline 342 having tooth missing portions formed in a carrier, clutch discs 61 fitted in the female involute spline, a piston 63 for pressing the clutch discs 61 and a thrust bearing 65 that is disposed between the clutch discs and the piston and comprises a race 652 having a pawl piece engaged with the female involute spline, wherein the involute spline is shaped so that the engagement surface of the pawl piece corresponds to the engagement surface of the female involute spline.

Description

  The present invention relates to a stationary cylinder type clutch device used for a continuously variable transmission (CVT), a stepped automatic transmission (AT), or the like.

  In general, a clutch device used for a continuously variable transmission or the like receives a hydraulic pressure from a hub and a drum constituting an input / output rotating member, a clutch plate disposed between the outer periphery of the hub and the inner periphery of the drum, It is comprised with the piston which fastens a clutch board. In a stationary cylinder type clutch device, a piston is provided on a fixed member, and a pressing force of the piston is transmitted to a clutch plate that rotates through a thrust bearing (see, for example, Patent Documents 1 and 2).

JP 2007-113684 A Japanese Patent No. 3852143

  In the stationary cylinder type clutch device, the thrust bearing race is rotated integrally with the drum and / or the carrier by engaging a claw piece provided on the outer peripheral portion thereof with the female involute spline in the carrier. Yes.

  However, since the meshing surface 72 of the female involute spline 71 of the carrier 70 is inclined as shown in FIG. 11, the claw piece 81 of the race 80 rises straight from the root in the radial direction. The edge 81 a of the piece 81 abuts on the meshing surface 72 of the female involute spline 71. In particular, when the relative rotational direction of the race 80 and the carrier 70 is reversed by switching the shift range or the like, the edge 81a of the claw piece 81 collides with the meshing surface 72 of the female involute spline 71. May wear out. Further, if a light alloy such as an aluminum alloy is adopted for the carrier 70 for weight reduction, the above-described wear may be further promoted.

  The present invention was devised in view of the above-described problems, and is a stationary device that suppresses wear of a rotating body such as a carrier by contacting with a claw piece provided on an outer peripheral portion of a thrust bearing race. An object of the present invention is to provide a cylinder type clutch device.

  As means for solving the above-described problems, the stationary cylinder type clutch device of the present invention is configured as follows.

  That is, the stationary cylinder type clutch device of the present invention includes a female involute spline having a toothless portion formed in a rotating body that rotates about an input shaft, a clutch plate fitted to the female involute spline, and the input shaft. A race that is provided so as to be non-rotatable around and receives a hydraulic pressure to press the clutch plate, and is disposed between the clutch plate and the piston, and has a claw piece engaged with the female involute spline. And a thrust bearing configured to include an involute spline shape corresponding to the meshing surface of the female involute spline. Distributed in a plurality of regions set at substantially equal intervals on the outer periphery of each of the regions. A plurality of small claw pieces formed at the same pitch as that of the involute spline and / or a large claw piece formed so as to be fitted to a missing tooth portion of the female involute spline. To do.

  According to the stationary cylinder type clutch device having such a configuration, the meshing surfaces of the claw pieces of the race are involute spline shapes corresponding to the meshing surfaces of the female involute splines of the rotating body. It becomes larger and wear on the rotating body side due to the claw pieces of the race is suppressed.

  Further, since the involute spline has a centering effect during torque transmission, the shift of the rotation center of the thrust bearing is corrected. As a result, the life of the thrust bearing is extended.

  Also, by making the meshing surface of the claw pieces of the race into an involute spline shape, the gap between the rotating body and the female involute spline is reduced, and the amount of lubricating oil that passes between the race and the rotating body passes through. It becomes easy to make a proper amount.

  According to the stationary cylinder type clutch device of the present invention, the engagement surface of the claw piece of the race has an involute spline shape corresponding to the engagement surface of the female involute spline of the rotating body. Wear on the body side is suppressed. As a result, it is possible to reduce the component cost and reduce the weight of the component.

1 is a diagram showing a schematic configuration of a vehicle equipped with a continuously variable transmission including a stationary cylinder type clutch device according to an embodiment of the present invention. It is an expansion detailed sectional view of the Z section of Drawing 1. It is the figure which looked at the race of the thrust bearing which concerns on embodiment of this invention from the axial direction engine side. It is AA sectional drawing of FIG. It is the figure which looked at the carrier from the axial direction engine side. It is BB sectional drawing of FIG. It is the figure seen from the axial direction engine side which shows the state which fitted the race of the thrust bearing in the carrier. It is the elements on larger scale which show the state which the race which concerns on embodiment of this invention fitted to the female involute spline of the carrier. It is the figure which looked at the race of the thrust bearing which concerns on other embodiment of this invention from the axial direction engine side. It is the figure which looked at the race of the thrust bearing which concerns on other embodiment of this invention from the axial direction engine side. It is the elements on larger scale showing the state where the race concerning the conventional example engaged with the female involute spline of the carrier.

  Hereinafter, a stationary cylinder type clutch device according to an embodiment of the present invention will be described with reference to the drawings. The stationary cylinder type clutch device is used for a continuously variable transmission (CVT), a stepped automatic transmission (AT), and the like. The following example demonstrates the case where a stationary cylinder type clutch apparatus is applied to a belt-type continuously variable transmission.

  FIG. 1 shows a schematic configuration of a vehicle equipped with a belt type continuously variable transmission. The vehicle shown in FIG. 1 is an FF (front engine / front drive) type vehicle, and includes an engine 1, a torque converter 2, a forward / reverse switching device 3, a belt-type continuously variable transmission 4, a reduction gear device 5, a differential gear. A gear device 6 and the like are mounted.

  A crankshaft 11, which is an output shaft of the engine 1, is connected to the torque converter 2, and the output of the engine 1 is transmitted from the torque converter 2 to the forward / reverse switching device 3, the belt type continuously variable transmission 4, and the reduction gear device 5. To the differential gear device 6 and distributed to the left and right drive wheels (not shown).

  The torque converter 2 includes a pump impeller 21 on the input shaft side, a turbine runner 22 on the output shaft side, a stator 23 that exhibits a torque amplification function, and a one-way clutch 24, and is provided between the pump impeller 21 and the turbine runner 22. The power is transmitted through the fluid. The torque converter 2 is provided with a lockup clutch 25 that directly connects the input side and the output side thereof. Further, the torque converter 2 is provided with a mechanical oil pump 7 that is connected to and driven by a pump impeller 21.

  The forward / reverse switching device 3 includes a planetary gear mechanism 30, a forward clutch 60 (stationary cylinder type clutch device), and a reverse brake 50. The planetary gear mechanism 30 illustrated in FIG. 1 is of a single pinion type, in which a sun gear 31 is connected to the turbine shaft 28 and a ring gear 32 is connected to the input shaft 40 of the belt type continuously variable transmission 4. The reverse brake 50 is for stopping the rotation of the carrier 34, and the forward clutch 60 is for fastening the carrier 34 and the sun gear 31 that rotatably support the pinion gear 33 to rotate together. .

  When the forward clutch 60 is released and the reverse brake 50 is engaged, the rotation of the turbine shaft 28 is reversed and decelerated and transmitted to the input shaft 40. On the other hand, when the reverse brake 50 is released and the forward clutch 60 is engaged, the carrier 34 and the sun gear 31 of the planetary gear mechanism 30 rotate together, and the turbine shaft 28 and the input shaft 40 are directly connected. When both the forward clutch 60 and the reverse brake 50 are released, the forward / reverse switching device 3 cuts off the power and forms a neutral state.

  The belt type continuously variable transmission 4 includes an input-side primary pulley 41, an output-side secondary pulley 42, and a metal belt 43 wound between the primary pulley 41 and the secondary pulley 42. .

  The primary pulley 41 is a variable pulley having a variable effective diameter, and a fixed sheave 411 fixed to the input shaft 40 and a movable sheave 412 disposed on the input shaft 40 in a state in which sliding is possible only in the axial direction. And is mainly composed. Similarly to the primary pulley 41, the secondary pulley 42 is a variable pulley having a variable effective diameter, and a fixed sheave 421 fixed to the output shaft 44 and a state in which the output shaft 44 can slide only in the axial direction. The movable sheave 422 is mainly configured.

  A hydraulic actuator 413 for changing the V groove width between the fixed sheave 411 and the movable sheave 412 is disposed on the movable sheave 412 side of the primary pulley 41. The V groove width is changed by controlling the hydraulic pressure supplied to the hydraulic actuator 413. Similarly, a hydraulic actuator 423 for changing the V groove width between the fixed sheave 421 and the movable sheave 422 is also arranged on the movable sheave 422 side of the secondary pulley 42, and is supplied to the hydraulic actuator 423. The V groove width is changed by controlling the hydraulic pressure.

  Hereinafter, the forward clutch 60 (hereinafter also simply referred to as “clutch 60”) which is a stationary cylinder type clutch device will be described in detail.

  As shown in FIGS. 1 and 2, a cylindrical portion 311 serving as a clutch hub is integrally projected on the front side (engine 1 side) of the sun gear 31. An inner diameter portion of the clutch plate 61 is splined to the outer periphery of the cylindrical portion 311.

  As shown in FIG. 2, a piston 63 having a U-shaped cross section is disposed on the rear side (on the side opposite to the engine 1) of the pump cover 8 that is a non-rotating fixing member. By pushing 61, the forward clutch 60 is fastened. A thrust bearing 65 is disposed between the clutch plate 61 and the piston 63 to transmit thrust while allowing relative rotation. A cushion spring 66 is interposed between the clutch plate 61 and the rim 341 of the carrier 34.

  The thrust bearing 65 includes a plurality of rollers 651, and the rollers 651 are rotatably held by a race 652 via a cage 653. A support plate 654 that is another race of the thrust bearing 65 is disposed on the rear side surface of the piston 63 that faces the roller 651.

  As shown in FIGS. 3 and 4, the race 652 has a cylindrical guide portion 6522 that is bent toward the piston 63 at the outer peripheral portion thereof and slidably contacts the tooth tip of the female involute spline 342 of the carrier 34. Is formed. In addition, a plurality of claw pieces 6521 are provided on the outer periphery of the race 652 so as to project in the radial direction.

  5 and 6 are diagrams illustrating an example of the carrier 34. FIG. A female involute spline 342 having a missing tooth portion 3421 is formed inside the carrier 34. The missing tooth portion 3421 is provided to form an insertion hole 343 for inserting a pin of the pinion gear 33 (see FIG. 1).

  FIG. 7 is a view showing a state in which a race 652 is fitted in the carrier 34. In FIG. 7, the portion of the race 652 is shaded in order to easily identify the race 652 and the carrier 34. As shown in this figure, the claw piece 6521 of the race 652 is engaged with a female involute spline 342 formed on the carrier 34 (rotating body), so that the race 652 rotates integrally with the carrier 34. It has become.

  As shown in FIG. 8, the claw piece 6521 of the race 652 has an involute spline shape whose meshing surface B1 corresponds to the meshing surface C1 of the female involute spline 342. For this reason, compared with the conventional claw piece 81 (see FIG. 11), the contact area of the carrier 34 with the meshing surface C1 of the female involute spline 342 is increased, and as a result, the carrier 34 has a side closer to the female involute spline 342. Abrasion is greatly suppressed.

  Further, as shown in FIG. 3, the claw pieces 6521 are distributed and formed in a plurality (four in FIG. 3) of regions F1 to F4 set at substantially equal intervals on the outer periphery of the race 652. A small claw piece 6521a or a large claw piece 6521b is formed in each region F1 to F4. The small claw piece 6521a is composed of a plurality of claw pieces 6521 formed at the same pitch as the female involute spline 342, and the large claw piece 6521b is formed so as to be fitted to the missing tooth portion 3421 of the female involute spline 342.

  According to the stationary cylinder type clutch device described above, the wear on the female involute spline 342 side of the carrier 34 is significantly suppressed as described above, and the following effects are also achieved.

  That is, since the involute spline has a centering action during torque transmission, the shift of the rotation center of the thrust bearing 65 is corrected. As a result, the life of the thrust bearing 65 is extended.

  Further, the involute shape of the claw piece 6521 of the race 652 enables overball diameter (OBD) management and BBD (Between ball diameter) management, and the claw piece 6521 of the race 652 and the female involute spline 342 of the carrier 34 It is possible to easily reduce the play in the rotational direction and the amount of misalignment.

  Further, by making the meshing surface B1 of the claw piece 6521 of the race 652 into an involute spline shape, the gap between the female involute spline 342 of the carrier 34 is reduced compared to the conventional one, and the race 652 and the carrier 34 are reduced. It becomes easy to make the passing oil amount of the lubricating oil passing between the two to an appropriate amount.

  In addition, the rotation balance of the race 652 is improved by setting the regions F1 to F4 at substantially equal intervals in the circumferential direction.

  Further, as shown in FIG. 3, only the small claw piece 6521a is formed on the upper side in the drawing, and the large claw piece 6521b and the small claw piece 6521a are arranged on the lower side in the drawing, so that the small claw piece 6521a and the large claw are arranged. By making the arrangement of the piece 6521b asymmetrical, it is possible to prevent erroneous assembly when the race 652 is assembled to the carrier 34.

<Other embodiments>
As shown in FIG. 9, in the race 652, all the locations corresponding to the tooth-missing portion 3421 of the female involute spline 342 of the carrier 34 may be the large claw piece 6521b. Further, as shown in FIG. 10, in the race 652, all the locations corresponding to the missing tooth portion 3421 of the female involute spline 342 of the carrier 34 may be the small claw pieces 6521 a. Further, in the above-described embodiment, the example in which the claw pieces 6521 are distributed and formed in the four regions F1 to F4 at substantially equal intervals on the outer periphery of the race 652 has been described as an example. Alternatively, it may be set at approximately equal intervals at five or more locations.

  Further, as the carrier 34, the race 652 in which the insertion holes 343 of the pin for the pinion gear 33 are provided at four positions at equal intervals in the circumferential direction and the tooth missing portion 3421 is formed corresponding to the four positions is exemplified. When a carrier having three or more holes 343 provided at equal intervals in the circumferential direction is employed, a race in which the large claw piece 6521b or the small claw piece 6521a is fitted in each of the missing tooth portions 3421 at the corresponding location is employed. do it.

  The present invention is applicable to, for example, a stationary cylinder type clutch device used for CVT, AT, and the like.

28 Turbine shaft (input shaft)
34 Carrier (Rotating body)
60 Forward clutch (stationary cylinder type clutch device)
61 Clutch plate 63 Piston 65 Thrust bearing 342 Female involute spline 652 Race 3421 Notch portion 6521 Claw piece 6521a Small claw piece 6521b Large claw piece B1 Race side meshing surface C1 Carrier side meshing surface F1 to F4 region

Claims (1)

A female involute spline having a missing tooth portion formed in a rotating body that rotates about an input shaft;
A clutch plate fitted to the female involute spline;
A piston that is non-rotatable about the input shaft and receives the supply of hydraulic pressure to press the clutch plate;
A thrust bearing disposed between the clutch plate and the piston and including a race having a claw piece engaged with the female involute spline;
In a stationary cylinder type clutch device comprising:
The meshing surface of the claw piece has an involute spline shape corresponding to the meshing surface of the female involute spline,
The claw pieces are distributed and formed in a plurality of regions set at substantially equal intervals on the outer periphery of the race,
In each of the regions, a plurality of small claw pieces formed at the same pitch as the female involute spline and / or a large claw piece formed so as to be fitted to a missing tooth portion of the female involute spline are formed. ing,
A stationary cylinder type clutch device