JP2012202438A - Planetary gear type power transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce a cost and quality control manhours, when controlling a clearance dimension of a friction plate of a multiplate frictional fastening element, while keeping stably a support rigidity of a thrust load by a carrier plate.SOLUTION: This planetary gear type power transmission is formed with a pressure receiving part for receiving a fastening load of an advance clutch 31, in the carrier plate 36 of a single pinion type planetary gear 30. In the planetary gear type power transmission, the friction plate of the advance clutch 31 is constituted of a plurality of driving plates 31a, 31a, 31a arranged alternately, and a plurality of driven plates 31B, 31b, 31b, one driven plate out of the plurality of driven plates 31B, 31b, 31b is set to the clearance regulating driven plate 31B selected to bring the clearance dimension L between the pressure receiving part of the carrier plate 36 and the driving plate 31a adjacent to the pressure receiving part, into a desired clearance dimension.

Description

  The present invention relates to a planetary gear type power transmission device in which a planetary gear and a multi-plate friction element are arranged in a power transmission system from a drive source.

  Conventionally, a planetary gear and a multi-plate friction clutch are arranged in the power transmission system from the drive source, the carrier supporting the pinion of the planetary gear is extended toward the clutch drum of the multi-plate friction clutch, and the extension end is snapped. The carrier plate is connected to the mounting position of the ring. And the planetary gear type power transmission device in which the pressure-receiving part which receives the fastening load of a multi-plate friction clutch was formed in the carrier plate is known (for example, refer patent document 1, 2).

Japanese Patent Laid-Open No. 11-63014 JP-A-9-89015

However, in the conventional planetary gear type power transmission device, as one of the roles of the retaining plate that receives the fastening load of the multi-plate friction clutch, the carrier plate has the role of a gap adjusting plate. For this reason, a plurality of carrier plates having different plate thicknesses are prepared, and one carrier plate having a plate thickness having a desired gap dimension is selected and assembled from among the plurality of carrier plates. The gap size between the abutting position) and the drive plate (clutch release position) adjacent to the carrier plate is managed. Therefore, it is necessary to prepare a plurality of carrier plates having different plate thicknesses due to large parts, and to select and assemble one of these plates, resulting in an increase in cost and quality control man-hours.
In addition, as a result of the carrier plate serving as a gap adjustment plate, a carrier plate having a different thickness is selected for each device, and the support rigidity of the thrust load by the carrier plate is kept constant (stable). I can't.

  The present invention has been made paying attention to the above-mentioned problems, and it is possible to control the cost and quality when managing the clearance dimension of the friction plate of the multi-plate friction fastening element while maintaining the support rigidity of the thrust load by the carrier plate stably. An object of the present invention is to provide a planetary gear type power transmission device capable of reducing the number of steps.

In order to achieve the above object, a planetary gear type power transmission device of the present invention includes a planetary gear and a multi-plate friction element arranged in a power transmission system from a drive source, and a carrier for supporting a pinion of the planetary gear. The plate friction element is extended toward the friction plate support member, and the extended end portion thereof is a carrier plate coupled to the attachment position of the snap ring, and the pressure receiving portion that receives the fastening load of the multi-plate friction element is provided on the carrier plate. Is formed.
In this planetary gear type power transmission device, the friction plate of the multi-plate friction element is constituted by a plurality of drive plates and a plurality of driven plates which are alternately arranged. And, for the gap adjustment, one driven plate of the plurality of driven plates is selected so that the gap between the pressure receiving portion of the carrier plate and the plate adjacent to the pressure receiving portion becomes a desired gap size. Set to driven plate.

Therefore, the role of the gap adjusting plate is replaced by the carrier plate, and one of the plurality of driven plates is given. For this reason, a plurality of driven plates having different plate thicknesses are prepared, and a single driven plate having a plate thickness having a desired gap dimension is selected and assembled from the plurality of driven plates. The gap size between the pressure receiving portion and a plate (for example, a drive plate) adjacent to the pressure receiving portion is managed.
Therefore, it is only necessary to prepare a plurality of driven plates having different thicknesses as compared with the carrier plate, and select and assemble one plate out of them, thereby reducing cost and quality control man-hours. Furthermore, since the carrier plate does not function as a gap adjusting plate and the thickness of the carrier plate is not changed, the support rigidity of the thrust load by the carrier plate is stably maintained.
As a result, it is possible to reduce costs and quality control man-hours when managing the gap size of the friction plate of the multi-plate friction fastening element while maintaining the support rigidity of the thrust load by the carrier plate stably.

1 is an overall drive system configuration diagram showing a drive system of an engine vehicle equipped with a belt type continuously variable transmission to which a planetary gear type power transmission device of Example 1 is applied. It is sectional drawing which shows the forward / reverse switching mechanism of the belt type continuously variable transmission to which the planetary gear type power transmission device of the first embodiment is applied. FIG. 3 is an enlarged cross-sectional view illustrating a configuration of a main part in which a single pinion planetary gear and a forward clutch are arranged in the planetary gear type power transmission device of the first embodiment. FIG. 4 is a view in the direction of arrow A in FIG. 3 showing details of the brake / clutch drum and the retaining plate portion of the planetary gear type power transmission device of the first embodiment. FIG. 4 is a view in the direction of the arrow B in FIG. 3 showing details of the brake / clutch drum and the retaining plate portion of the planetary gear type power transmission device of the first embodiment. FIG. 6 is an operation explanatory view showing an assembling operation of the forward clutch including clearance size management in the planetary gear type power transmission device of the first embodiment.

  Hereinafter, the best mode for realizing the planetary gear type power transmission device of the present invention will be described based on Example 1 shown in the drawings.

First, the configuration will be described.
FIG. 1 shows a drive system of an engine vehicle equipped with a belt type continuously variable transmission to which the planetary gear type power transmission device of the first embodiment is applied. Hereinafter, the overall structure of the drive system will be described with reference to FIG.

  As shown in FIG. 1, the drive system of an engine vehicle equipped with a belt type continuously variable transmission includes an engine 1, a torque converter 2, a forward / reverse switching mechanism 3, a belt type continuously variable transmission mechanism 4, and a final deceleration. A mechanism 5 and drive wheels 6 and 6 are provided.

  The engine 1 is provided as a drive source, and can control the engine speed and the fuel injection amount by an engine control signal from the outside, in addition to controlling the output torque by the driver's accelerator operation.

  The torque converter 2 is a fluid transmission device having a torque increasing function, and can lock the engine output shaft 11 (= torque converter input shaft) and the torque converter output shaft 21 directly when the torque increasing function is not required. 20 The torque converter 2 includes a turbine runner 23 connected to the engine output shaft 11 via a converter housing 22, a pump impeller 24 connected to the torque converter output shaft 21, and a stator 26 provided via a one-way clutch 25. , Is a component.

  The forward / reverse switching mechanism 3 is a mechanism that switches the input rotation direction of the rotational driving force input from the engine 1 to the belt type continuously variable transmission mechanism 4 between a forward rotation direction during forward travel and a reverse rotation direction during reverse travel. . The forward / reverse switching mechanism 3 includes a single pinion planetary gear 30, a forward clutch 31, and a reverse brake 32. In the first embodiment, a planetary gear type power transmission device is applied to the forward / reverse switching mechanism 3.

  The belt-type continuously variable transmission mechanism 4 is a continuously variable transmission that continuously changes a gear ratio, which is a ratio of the input rotational speed of the transmission input shaft 40 and the output rotational speed of the transmission output shaft 41, by changing the belt contact diameter. It has a function. The belt type continuously variable transmission mechanism 4 includes a primary pulley 42, a secondary pulley 43, and a belt 44. The primary pulley 42 includes a fixed pulley 42 a and a slide pulley 42 b, and the slide pulley 42 b slides with a primary pressure guided to the primary pressure chamber 45. The secondary pulley 43 includes a fixed pulley 43 a and a slide pulley 43 b, and the slide pulley 43 b is slid by a secondary pressure guided to the secondary pressure chamber 46. The belt 44 is wound around a pair of sheave surfaces that form a V shape of the primary pulley 42 and a pair of sheave surfaces that form a V shape of the secondary pulley 43.

  The final reduction mechanism 5 is a mechanism that decelerates the transmission output rotation from the transmission output shaft 41 of the belt-type continuously variable transmission mechanism 4 and transmits it to the left and right drive wheels 6 and 6 while providing a differential function. The final reduction mechanism 5 is interposed in the transmission output shaft 41, the idler shaft 50, and the left and right drive shafts 51, 51, and has a first gear 52, a second gear 53, a third gear 54 having a reduction function. And a fourth gear 55 and a differential gear 56 having a differential function.

  FIG. 2 shows a forward / reverse switching mechanism 3 of a belt type continuously variable transmission to which a planetary gear type power transmission device is applied. Hereinafter, the configuration of the forward / reverse switching mechanism 3 will be described with reference to FIG.

  As shown in FIG. 2, the forward / reverse switching mechanism 3 includes a single pinion planetary gear 30 (planetary gear), a forward clutch 31 (multi-plate friction element), a reverse brake 32, and a brake / clutch drum 33 (friction). Plate support member), a clutch hub 34, a transmission case 35, and a carrier plate 36.

  The single pinion planetary gear 30 includes a sun gear 30a, a ring gear 30b, a pinion 30c that meshes with the sun gear 30a and the ring gear 30b, and a carrier 30d that supports the plurality of pinions 30c. The sun gear 30 a is connected to the torque converter output shaft 21 and receives the rotational driving force that has passed through the engine 1 and the torque converter 2. The ring gear 30b is connected to the fixed pulley 42a of the primary pulley 42 via a ring gear plate 70, and the rotational driving force in the forward or reverse direction passing through the forward / reverse switching mechanism 3 is applied to the belt-type continuously variable transmission mechanism 4. Output to the primary pulley 42. The fixed pulley 42a is rotatably supported by a ball bearing 71 with respect to the transmission case 35.

  The forward clutch 31 guides the clutch pressure to the clutch pressure chamber 73 formed between the brake / clutch drum 33 and the clutch piston 72 during forward travel, so that the clutch piston 72 strokes in the left direction in FIG. A wet multi-plate clutch to be fastened. When the forward clutch 31 is engaged, the sun gear 30 a and the carrier 30 d of the single pinion planetary gear 30 are connected according to the fastening force of the forward clutch 31. The forward clutch 31 includes a drive plate 31a (for example, four) that is spline-fitted to the clutch hub 34 and a driven plate that is spline-fitted to the brake / clutch drum 33 so as to be movable in the axial direction. 31b (for example, 4 sheets) are arranged alternately. A return spring 76 is provided between the clutch piston 72 and the spring support plate 75 to apply a biasing force to the clutch piston 72 in the right direction in FIG. 2 when the forward clutch 31 is released.

  During reverse travel, the reverse brake 32 guides the brake pressure to a brake pressure chamber 78 formed between the transmission case 35 and the brake piston 77, whereby the brake piston 77 is stroked to the right in FIG. It is a wet multi-plate brake. When the reverse brake 32 is engaged, the carrier 30d of the single pinion planetary gear 30 is fixed to the transmission case 36 according to the engagement force of the reverse brake 32. The reverse brake 32 is spline-fitted with a drive plate 32a (for example, five) that is spline-fitted to the brake / clutch drum 33 so as to be movable in the axial direction, and is spline-fitted with respect to the transmission case 35. It is configured by alternately arranging driven plates 32b (for example, five plates). A return spring 80 is provided between the brake piston 77 and the spring support plate 79 to apply a biasing force to the brake piston 77 in the left direction in FIG. 2 when the reverse brake 32 is released.

  The carrier plate 36 extends the carrier supporting the pinion 30c of the single pinion planetary gear 30 toward the brake / clutch drum 33 in the outer diameter direction, and the extended end thereof is spline-fitted to the attachment position of the snap ring 81. It is a combined plate. That is, the carrier plate 36 has both a role of a carrier that supports the pinion 30c and a role of a retaining plate in which a pressure receiving portion that receives a fastening load of the forward clutch 31 is formed.

  FIGS. 3-5 shows the principal part structure by which the forward clutch 31 slip-engaged with the single pinion type planetary gear 30 is arrange | positioned in the planetary gear type power transmission device of Example 1. FIG. Hereinafter, based on FIGS. 3-5, the principal part structure of the planetary gear type power transmission device of Example 1 is demonstrated in detail.

  The sun gear 30a of the single pinion planetary gear 30 has a first thrust bearing 82 interposed between the left side surface of FIG. 3 and the ring gear plate 70, and the clutch hub 34 is fixed to the right side surface position of FIG. A spline portion 30e coupled to the torque converter output shaft 21 is formed on the inner peripheral surface of the sun gear.

  The ring gear 30b of the single pinion planetary gear 30 has a ring gear plate 70 fixed at the left side surface position in FIG. 3, and a spline portion 70a coupled to the fixed pulley 42a of the primary pulley 42 on the inner peripheral surface of the ring gear plate 70. Is formed.

  The pinion 30c of the single pinion planetary gear 30 is rotatably supported by a pinion shaft 74 via a needle bearing 83, and a first thrust washer 84 is fitted to the left side surface position of FIG. A second thrust washer 85 is fitted at the surface position. 3, the carrier 30d is fixed to the pinion shaft 74 with the first thrust washer 84 sandwiched therebetween, and the carrier plate 36 is secured to the pinion shaft 74 with the second thrust washer 85 sandwiched therebetween on the right side of FIG. It is fixed.

  As shown in FIGS. 4 and 5, the brake / clutch drum 33 is formed with spline inner teeth 33a fitted to the driven plate 31b of the forward clutch 31 on the inner surface side of the cylindrical drum, and retreated on the outer surface side. Spline external teeth 33b that fit with the drive plate 32a of the brake 32 are formed. 4 and 5, an annular snap ring groove 33c is formed at the inner surface position to which the snap ring 81 is attached, and the inner side in the axial direction from the end surface position to about four locations on the circumference on the snap ring 81 side. A plate-abutting groove 33d cut into is formed. The carrier plate 36 omits the formation of spline teeth at positions corresponding to the plate abutting grooves 33d among the spline teeth on the entire circumference. That is, in the hatching region C of FIG. 5, the movement in the axial direction is restricted by abutting the carrier plate 36 against the plate abutting groove 33d. For this reason, as shown in FIG. 3, the carrier plate 36 has a range from the axial movement restriction position due to contact with the snap ring 81 to the axial movement restriction position due to abutment against the plate abutment groove 33d. It is determined as the allowable movement range in the axial direction.

The forward clutch 31 is constituted by four drive plates 31a, 31a, 31a, 31a and four driven plates 31B, 31b, 31b, 31b which are alternately arranged. Of the four driven plates 31B, 31b, 31b, 31b, one driven plate is set as the gap adjusting driven plate 31B. The driven plate 31B for adjusting the gap includes a pressure receiving portion of the carrier plate 36 and a drive plate 31a adjacent to the pressure receiving portion among a plurality of driven plates 31B1, 31B2, 31B3, 31B4,. One plate selected such that the gap dimension is a desired gap dimension L. Of the four driven plates 31B, 31b, 31b, 31b, the driven plate closest to the carrier plate 36 is the driven plate 31B for adjusting the gap.
Here, the plurality of driven plates 31B1, 31B2, 31B3, 31B4,... Prepared as the gap adjusting driven plate 31B have different minimum thicknesses from those of the other driven plates 31b, 31b, 31b. Also set thick. Further, the gap adjusting driven plate 31B is set to have a lower thermal conductivity than that of the other driven plates 31b, 31b, and 31b by material selection, processing, or the like.

Next, the operation will be described.
The operation of the planetary gear type power transmission device according to the first embodiment will be described by dividing it into “forward / reverse switching operation”, “forward clutch assembly operation”, and “forward clutch fastening operation”.

[Forward / backward switching]
The forward / reverse switching operation between forward travel by fastening the forward clutch 31 and reverse travel by fastening the reverse brake 32, which is performed by the forward / backward switching mechanism 3 to which the planetary gear type power transmission device of the first embodiment is applied. explain.

At the time of forward traveling by the N → D selection operation, the clutch piston 72 strokes to the left in FIG. 2 by guiding the clutch pressure to the clutch pressure chamber 73, and the released forward clutch 31 is moved to the clutch pressure chamber 73. It is fastened according to the magnitude of the clutch pressure.
When the forward clutch 31 is engaged, the sun gear 30a and the carrier 30d of the single pinion planetary gear 30 are connected to the forward clutch 31 via the clutch hub 34 → forward clutch 31 → brake / clutch drum 33 → carrier plate 36 → pinion shaft 74. They are connected according to the fastening force.
For this reason, when the forward clutch 31 is completely engaged, the three rotating members (the sun gear 30a, the ring gear 30b, and the carrier 30d) of the single pinion planetary gear 30 rotate together and rotate together. That is, the output rotation to the ring gear 30b that transmits the rotational driving force to the primary pulley 42 is the positive rotation at the same rotational speed in the same direction as the input rotation input to the sun gear 30a via the engine 1 and the torque converter 2. .

At the time of reverse traveling by the N → R selection operation, the brake piston 77 strokes to the right in FIG. 2 by introducing the brake pressure to the brake pressure chamber 78, and the released reverse brake 32 is applied to the brake pressure chamber 78. It is fastened according to the magnitude of the brake pressure.
When the reverse brake 32 is engaged, the carrier 30d of the single pinion planetary gear 30 is transmitted through the pinion shaft 74 → the carrier plate 36 → the brake / clutch drum 33 → the reverse brake 32 according to the engagement force of the reverse brake 32. It is fixed to the case 36.
For this reason, when the reverse brake 32 is completely engaged, among the three rotating members (sun gear 30a, ring gear 30b, carrier 30d) of the single pinion planetary gear 30, the carrier 30d is fixed, so that the sun gear 30a and the ring gear 30b are fixed. Different rotation directions. That is, the output rotation to the ring gear 30b that transmits the rotational driving force to the primary pulley 42 is the reverse rotation at a different rotational speed in the reverse direction to the input rotation input to the sun gear 30a via the engine 1 and the torque converter 2. .

[Forward clutch assembly]
The forward clutch 31 that is engaged during forward traveling cannot avoid variations in the gap dimension L in the assembled state due to variations in components. For this reason, when assembling the forward clutch 31, it is necessary to eliminate the variation in the gap dimension L. Hereinafter, the assembly operation of the forward clutch 31 reflecting this will be described with reference to FIG.

  The forward clutch 31 includes (a) a procedure for assembling the clutch drum 33 and the clutch hub 34, (b) a procedure for assembling the drive plate 31a and the driven plate 31b, (c) a procedure for adjusting the clearance dimension, and (d) a procedure for assembling the carrier plate 36. It is assembled by the procedure. Each procedure will be described below.

(a) Assembly procedure of clutch drum 33 and clutch hub 34 A clutch piston 72, a spring support plate 75, and a return spring 76 are assembled to the clutch drum 33. Then, the clutch hub 34 to which the sun gear 30 a is fixed integrally is assembled to the inner position of the clutch drum 33. By assembling the clutch drum 33 and the clutch hub 34, the annular spline inner teeth 33a and the spline outer teeth 34a face each other, and the drive plate 31a and the driven plate 31b can be assembled.

(b) Assembling procedure of drive plate 31a and driven plate 31b After assembling the clutch drum 33 and the clutch hub 34, first, the driven plate 31b is spline-coupled to the spline inner teeth 33a, and the clutch piston 72 is connected to the clutch piston 72. Insert until touching. Next, the drive plate 31a is spline-coupled to the spline external teeth 34a, and is inserted to a position where it comes into contact with the already assembled driven plate 31b. Next, the driven plate 31b is spline-coupled to the spline inner teeth 33a and inserted to a position where it comes into contact with the drive plate 31a already assembled.
Subsequently, the drive plate 31a, the driven plate 31b, and the drive plate 31a are assembled in order by the same assembling method. Then, the gap adjusting driven plate 31B is spline-coupled to the spline external teeth 34a, and is inserted to a position in contact with the drive plate 31a already assembled.

(c) Adjustment procedure of gap size After assembling the three drive plates 31a, the three driven plates 31b, and the one gap adjustment driven plate 31B, the plate of the brake / clutch drum 33 is assembled as described above. From the position of the abutting groove 33d (= the abutting position of the carrier plate 36), the gap dimension L ′ according to the position of the plate surface of the gap adjusting driven plate 31B is measured.
As shown in FIG. 3, the gap dimension L that needs to be managed is the gap dimension between the pressure receiving portion of the carrier plate 36 and the drive plate 31a adjacent to the pressure receiving portion. However, before the assembly of the carrier plate 36 and the drive plate 31a, in order to facilitate the measurement of the gap dimension, the gap dimension L ′ from the abutment position of the carrier plate 36 to the position of the plate surface of the gap adjustment driven plate 31B. To manage.
When the measured gap dimension L ′ coincides with a predetermined design dimension Ls at the time of assembly, or when it is within the allowable range of the design dimension Ls, the gap adjustment driven plate 31B that has already been assembled is used. The adjustment of the gap dimension L ′ is completed without replacement.
On the other hand, when the measured gap dimension L ′ is out of the predetermined allowable range of the design dimension Ls, the dimension error ΔL is calculated by subtracting the measured gap dimension L ′ from the design dimension Ls. When this dimensional error ΔL is known, one plate having a thickness that falls within the allowable range of the design dimension Ls is selected from the plurality of driven plates 31B1, 31B2, 31B3, 31B4,. Then, the adjustment of the gap dimension L ′ is completed by performing the plate replacement operation of removing the gap adjustment driven plate 31B that has already been assembled and installing the newly selected gap adjustment driven plate 31B.

(d) Assembly procedure of carrier plate 36 As described above, when the clearance dimension adjustment procedure for setting the clearance dimension L ′ within the allowable range of the design dimension Ls is completed, first, the last one drive plate 31a is removed from the spline. The splines are connected to the teeth 34a and inserted to a position where they come into contact with the already-adjusted gap adjusting driven plate 31B.
Next, the pinion assembly having the carrier plate 36 is spline-coupled to the spline inner teeth 33a while the sun gear 30a and the pinion 30c are engaged with each other.
Next, assembling of the carrier plate 36 is completed by fitting the snap ring 81 into the snap ring groove 33c so that the pinion assembly having the carrier plate 36 does not come off. Note that the ring gear plate 70 having the ring gear 30b is assembled while the gears mesh with the pinion 30c.

  As described above, in the first embodiment, of the four driven plates 31B, 31b, 31b, and 31b, one driven plate is connected to the pressure receiving portion of the carrier plate 36 and the drive plate 31a adjacent to the pressure receiving portion. A configuration is adopted in which the gap adjustment driven plate 31B is selected so that the gap dimension L becomes a desired gap dimension.

  That is, instead of the carrier plate 36, the gap adjusting plate functions as one of the plurality of driven plates 31B, 31b, 31b, 31b. Therefore, a plurality of driven plates 31B1, 31B2, 31B3, 31B4,... Having different plate thicknesses are prepared, and the gap dimension L is a desired gap dimension among the plurality of driven plates 31B1, 31B2, 31B3, 31B4,. One driven plate (= gap adjusting driven plate 31B) having a plate thickness to be selected is selected and assembled. As described above, by performing assembly work including selection of the gap adjustment driven plate 31B, the gap dimension L between the pressure receiving portion of the carrier plate 36 and the drive plate 31a adjacent to the pressure receiving portion becomes a desired gap size. It will fit. In other words, quality control is performed to keep the plate gap at the time of releasing the clutches of the many forward clutches 31 to be commercialized regardless of the variation of the components.

  Therefore, a plurality of driven plates 31B1, 31B2, 31B3, 31B4,..., Which are small parts compared to the carrier plate 36, are prepared. Then, the gap dimension L is managed to be constant only by selecting and assembling one plate from the prepared plurality of driven plates 31B1, 31B2, 31B3, 31B4,. As a result, costs and quality control man-hours are reduced as compared with the case where the carrier plate 36 has the role of the gap adjusting plate.

  Furthermore, the carrier plate 36 does not serve as a gap adjusting plate, and the thickness of the carrier plate 36 is not changed. For this reason, when the forward clutch 31 is engaged, a large thrust load acts on the carrier plate 36, but the support rigidity of the thrust load by the carrier plate 36 is kept constant and stable.

  In the first embodiment, a configuration is adopted in which the driven plate closest to the carrier plate 36 among the four driven plates 31B, 31b, 31b, 31b is the gap adjusting driven plate 31B.

  For example, one driven plate at a position away from the carrier plate 36 is defined as a gap adjusting driven plate 31B. In this case, when the gap adjustment driven plate 31B that is first assembled is replaced with the newly selected gap adjustment driven plate 31B, it is necessary to simultaneously replace the drive plate 31a and the driven plate 31b that have already been assembled. Yes, it takes time and effort to replace it.

  In contrast, in the first embodiment, when the gap adjustment driven plate 31B that is first assembled is replaced with the newly selected gap adjustment driven plate 31B, the three drive plates 31a that have already been assembled are It is only necessary to replace the gap adjusting driven plate 31B while leaving the three driven plates 31b as they are. That is, the labor for exchanging the gap adjusting driven plate 31B is saved.

[Forward clutch engagement]
As described above, one of the plurality of driven plates constituting the forward clutch 31 is used as the gap adjusting driven plate 31B. For this reason, it is necessary to eliminate the influence of adding the gap adjustment driven plate 31B. Hereinafter, the fastening operation of the forward clutch 31 reflecting this will be described.

  In the first embodiment, the minimum plate thickness of the plurality of driven plates 31B1, 31B2, 31B3, 31B4,... Prepared as the gap adjusting driven plate 31B is set larger than the plate thickness of the other driven plates 31b, 31b, 31b. The configuration to adopt was adopted.

  For example, the plate thickness average value of the plurality of driven plates 31B1, 31B2, 31B3, 31B4,... Prepared as the gap adjusting driven plate 31B is set to the plate thickness of the other driven plates 31b, 31b, 31b. In this case, when one gap adjustment driven plate 31B is selected so that the gap dimension L becomes a desired gap dimension, the gap adjustment driven having a plate thickness thinner than the plate thickness of the other driven plates 31b, 31b, 31b. The plate 31B may be selected. As described above, when the gap adjusting driven plate 31B having a small plate thickness is selected, the friction plate rigidity of the forward clutch 31 is lower than the desired rigidity.

  On the other hand, if the minimum plate thickness of the prepared plurality of driven plates 31B1, 31B2, 31B3, 31B4,... Is set thicker than the plate thicknesses of the other driven plates 31b, 31b, 31b, the plate with the minimum plate thickness is assumed. However, even if the clearance adjustment driven plate 31B is selected, the friction plate rigidity of the forward clutch 31 becomes higher than the desired rigidity. When a plate other than the minimum plate thickness is selected as the gap adjustment driven plate 31B, the friction plate rigidity of the forward clutch 31 becomes higher than the desired rigidity. In other words, the desired friction plate rigidity when the forward clutch 31 is engaged, regardless of which of the prepared driven plates 31B1, 31B2, 31B3, 31B4,... Is selected as the gap adjustment driven plate 31B. Is secured.

  In Example 1, the structure which sets the heat conductivity which transmits the heat | fever of the gap adjustment driven plate 31B lower than the heat conductivity of the other driven plates 31b, 31b, and 31b was employ | adopted.

  For example, when the forward clutch 31 is a clutch that frequently uses slip engagement, when the slip engagement is continued, the forward clutch 31 generates heat due to frictional heat. The heat generated in the forward clutch 31 is transmitted from the gap adjusting driven plate 31B at the end position to the drive plate 31a → the carrier plate 36 → the pinion shaft 74 → the needle bearing 83, thereby raising the temperature of the pinion assembly. For this reason, the durability reliability of the single pinion planetary gear 30 is lowered, for example, the life of the pinion assembly is shortened.

  In contrast, by setting the thermal conductivity of the gap adjusting driven plate 31B to be lower than the thermal conductivity of the other driven plates 31b, 31b, 31b, the heat generated in the forward clutch 31 is reduced at the end position. When the gap adjusting driven plate 31B is transmitted to the carrier plate 36 via the drive plate 31a, the heat transfer amount is kept low. That is, the durability reliability of the single pinion planetary gear 30 against the heat generated by the forward clutch 31 is improved.

Next, the effect will be described.
In the planetary gear type power transmission device of the first embodiment, the effects listed below can be obtained.

(1) A planetary gear (single pinion type planetary gear 30) and a multi-plate friction element (forward clutch 31) are arranged in a power transmission system from a drive source (engine 1), and the carrier 30d supports the pinion 30c of the planetary gear. Is extended toward the friction plate support member (brake / clutch drum 33) of the multi-plate friction element, and the extended end portion is coupled to the attachment position of the snap ring 81, and the carrier plate 36 is attached to the carrier plate 36. In the planetary gear type power transmission device in which a pressure receiving portion that receives the fastening load of the multi-plate friction element is formed,
A friction plate of the multi-plate friction element (advance clutch 31) is composed of a plurality of drive plates 31a, 31a, 31a, 31a and a plurality of driven plates 31B, 31b, 31b, 31b arranged alternately, Of the driven plates 31B, 31b, 31b, 31b, one driven plate is formed such that the gap dimension L between the pressure receiving portion of the carrier plate 36 and the plate (drive plate 31a) adjacent to the pressure receiving portion is a desired gap size. It was set to the gap adjustment driven plate 31B selected to be.
For this reason, the friction plate (drive plates 31a, 31a, 31a, 31a, driven plates 31B, 31b, 31b) of the multi-plate frictional engagement element (advance clutch 31) is maintained while maintaining the support rigidity of the thrust load by the carrier plate 36 stably. , 31b), the cost and the quality control man-hour can be reduced.

(2) The gap adjusting driven plate 31B is a driven plate at an end position closest to the carrier plate 36 among the plurality of driven plates 31B, 31b, 31b, 31b.
For this reason, in addition to the effect of (1), when exchanging the gap adjustment driven plate 31B, the drive plates 31a, 31a, 31a and the driven plates 31b, 31b, 31b that have already been assembled are left in the gap adjustment. It is only necessary to replace the driven plate 31B, and the labor for the replacement work can be saved.

(3) Among the selected plate thicknesses, the gap adjusting driven plate 31B has a minimum plate thickness set larger than the plate thicknesses of the other driven plates 31b, 31b, 31b.
For this reason, in addition to the effect of (1) or (2), even if any of the prepared driven plates 31B1, 31B2, 31B3, 31B4,... Is selected as the gap adjustment driven plate 31B, A desired friction plate rigidity when the multi-plate friction element (forward clutch 31) is fastened can be ensured.

(4) The clearance-adjusted driven plate 31B has a heat conductivity for transferring heat set lower than that of the other driven plates 31b, 31b, 31b.
For this reason, in addition to the effect of (2) or (3), the amount of heat transferred to the carrier plate 36 is kept low, so that the frictional heat generated by slip engagement of the multi-plate friction element (forward clutch 31) can be prevented. The durability reliability of the planetary gear (single pinion planetary gear 30) can be improved.

  As described above, the planetary gear type power transmission device of the present invention has been described based on the first embodiment. However, the specific configuration is not limited to the first embodiment, and the claims relate to each claim. Design changes and additions are allowed without departing from the scope of the invention.

  In the first embodiment, the multi-plate friction element is the forward clutch 31 having a multi-plate structure. However, the multi-plate friction element may be a reverse brake having a multi-plate structure, a shift clutch, a shift brake, or the like.

  In the first embodiment, an example in which the friction plate supporting member is the brake / clutch drum 33 that serves both as a brake drum and a clutch drum has been described. However, the friction plate support member may be a clutch drum, a brake drum, a clutch hub, or the like that supports the friction plate.

  In Example 1, the example of the carrier plate 36 by 1 component structure was shown. However, the carrier plate may be divided into two or more parts (for example, divided into a retaining plate part and a pinion carrier part) and splined so that power can be transmitted at each divided part. good.

  In the first embodiment, the planetary gear type power transmission device of the present invention is applied to the forward / reverse switching mechanism of the belt type continuously variable transmission. However, the planetary gear type power transmission device of the present invention can also be applied to a sub-transmission of a belt-type continuously variable transmission, a gear train of an automatic transmission (step AT) having a plurality of shift stages, and the like. In short, the present invention can be applied to a power transmission system from a driving source in which a planetary gear and a multi-plate friction element are arranged.

  In the first embodiment, the planetary gear type power transmission device of the present invention is applied to an engine vehicle having an engine as a drive source. However, the planetary gear type power transmission device of the present invention can be applied not only to an engine vehicle but also to a hybrid vehicle having an engine and a motor as a drive source and an electric vehicle having a motor as a drive source. In short, any vehicle including a planetary gear type power transmission device can be applied.

1 Engine (drive source)
2 Torque converter 3 Forward / reverse switching mechanism 4 Belt type continuously variable transmission mechanism 5 Final reduction mechanism 6, 6 Drive wheel 30 Single pinion planetary gear (planetary gear)
30a Sun gear 30b Ring gear 30c Pinion 30d Carrier 31 Forward clutch (multi-plate friction element)
31a Drive plate (friction plate)
31b Driven plate (friction plate)
31B Drive plates 31B1, 31B2, 31B3, 31B4 for adjusting clearances Multiple driven plates 32 Reverse brake 33 Brake / clutch drum (friction plate support member)
34 Clutch hub 35 Transmission case 36 Carrier plate L Clearance dimension

Claims (4)

A planetary gear and a multi-plate friction element are arranged in a power transmission system from a driving source, and a carrier that supports a pinion of the planetary gear extends toward a friction plate support member of the multi-plate friction element, and an extended end portion thereof In a planetary gear type power transmission device in which a pressure plate receiving a fastening load of the multi-plate friction element is formed on the carrier plate.
The friction plate of the multi-plate friction element is constituted by a plurality of drive plates and a plurality of driven plates arranged alternately, and one driven plate of the plurality of driven plates is connected to the pressure receiving portion of the carrier plate. A planetary gear type power transmission device, wherein a gap adjusting driven plate is selected so that a gap between the pressure receiving portion and a plate adjacent to the pressure receiving portion becomes a desired gap. In the planetary gear type power transmission device according to claim 1,
The planetary gear type power transmission device, wherein the gap adjusting driven plate is a driven plate at an end position closest to the carrier plate among the plurality of driven plates. In the planetary gear type power transmission device according to claim 1 or 2,
The planetary gear type power transmission device characterized in that the driven plate for adjusting the gap is set such that the minimum plate thickness among the selected plate thicknesses is larger than the plate thicknesses of the other driven plates. In the planetary gear type power transmission device according to claim 2 or 3,
The planetary gear type power transmission device, wherein the gap adjusting driven plate has a heat conductivity for transferring heat lower than that of other driven plates.