JPH1163014A - Planetary gear type power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the width or length of a power transmission device without decreasing its durability and a functional property. SOLUTION: For a forward and reverse movement switching device 23 which transmits power from an engine to a continuously variable transmission 22 with normal or reverse run, a planetary gear 31 and a forward clutch 30 are provided. When operating load is applied to the multiple disc clutch 30f of a forward clutch 30, the multiple disc clutch 30f is coupled with reaction force from a retaining plate 30h provided on the opposite side of the multiple disc clutch 30f and a load supporting face 31e formed on a planetary carrier 31d supporting a planetary pinion 31c. The retaining plate 30h which is supported by the whole load supporting face 31e formed on the planetary carrier 31d is reinforced so that the thickness of the retaining plate 30h can be relatively reduced or the retaining plate 30h itself can be eliminated.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear type power transmission device provided in a power transmission system for simplifying the structure of a friction engagement member for controlling transmission and reception of power.

[0002]

2. Description of the Related Art At present, planetary gears are used in various parts of a power transmission system of a vehicle. For example, a power transmission device incorporating a continuously variable transmission is employed as a forward / reverse switching device, a power transmission device incorporating a multi-stage transmission is employed as a transmission mechanism, and a four-wheel drive vehicle is provided with a front / rear transmission. It is adopted to actively control the torque distribution to the wheels.

[0003] In a power transmission device incorporating a continuously variable transmission,
A planetary gear type forward / reverse switching device is provided between a starting device including a torque converter and the continuously variable transmission, or
It is interposed between the continuously variable transmission and the output shaft connected to the axle. FIG. 10 shows an example in which the forward / reverse switching device is interposed between the starting device and the input shaft of the continuously variable transmission.

During forward running, a forward clutch 2 provided on a forward / reverse switching device 1 is connected, and a clutch drum 4 and a clutch hub 5 connected to an output shaft 3 extending from a starting device are connected. Pulley input shaft 6 extending from primary pulley 6 of the continuously variable transmission continuously connected to
The driving force in the normal rotation direction is transmitted to a.

On the other hand, when the vehicle is traveling in reverse, the forward clutch 2 is released and the reverse brake 8 is engaged. Then, the ring gear 9 constituting the planetary gear provided in the forward / reverse switching device 1 is fixed, and the planetary pinion 11 rotates via the planetary carrier 10 connected to the clutch drum 4, and meshes with the planetary pinion 11. The primary pulley 6 rotates in the opposite direction while being decelerated at a predetermined speed via the pulley input shaft 6a.

The operation of the planetary gear type forward / reverse switching device is disclosed, for example, in Japanese Patent Publication No. 3-72857.

[0007]

When an engine and a power transmission device integrally mounted on the engine are mounted horizontally in an engine room provided at a front portion of a vehicle body, for example, the width or length of the engine and the power transmission device are set. Must be of a size that can be stored in the engine room.

However, recent engine rooms are provided with frames on both sides for absorbing the impact of a collision.
A front tire is provided outside the frame. The frame needs to have a certain cross-section sufficient to maintain the steering stability of the vehicle and to maintain the rigidity in order to guarantee the collision safety. It is necessary to set a large turning angle in order to secure the steering performance.

In order to sufficiently satisfy both the volume of the engine room and the steering angle of the front tire, it is sufficient to increase the size of the vehicle body. However, it is not possible to increase the size of the vehicle body only to satisfy these requirements. However, simply increasing the weight of the vehicle, lowering the maneuverability, and hindering the efficiency of the drive system and deteriorating the fuel efficiency are not feasible.

As a result, the volume in the engine room tends to be relatively narrowed, and it is necessary to reduce the width or the length of the engine and the power transmission device inevitably.

As means for reducing the width or length of the power transmission device, for example, a forward clutch 2 shown in FIG.
A notch is formed in the retaining plate 13 which receives the reaction force of the clutch piston 12 which applies a coupling force to the outside of the retaining plate 13 by the thickness of the snap ring 14 which is engaged with the outside of the retaining plate 13. It is conceivable that the width or length of the power transmission device is reduced by at least the thickness of the snap ring 14 by immersing the snap ring 14 in the above.

Generally, the snap ring 14 merely hangs on the outer edge of the retaining plate 13. To withstand a large operating load from the clutch piston 12, the thickness of the retaining plate 13 itself must be reduced. ,
The rigidity is ensured by setting it to twice or more as compared with the other clutch drive plates 2a provided in the forward clutch 2, and the snap ring 14 is disengaged when the clutch is operated, and the contact surface pressure of the clutch drive plate 2a is increased. Is designed to prevent clutch wear and the like from deteriorating due to uniformity of the clutch.

Therefore, forming the notch for immersing the snap ring 14 in the retaining plate 13 not only lowers the rigidity but also causes the retaining plate 13 to be formed usually by pressing or the like. Thirteen processing steps increase, leading to an increase in manufacturing costs.

As shown in FIG. 10, the planetary carrier 10 is assembled to the clutch drum 4 by engaging a spline groove formed on the inner circumference of the clutch drum 4, so that the planetary carrier 10 can be easily disengaged. Therefore, these assemblies are individually performed in the final process with a thrust washer or the like interposed therebetween. as a result,
There is a problem that the assembly is complicated, the number of assembling steps is increased, and the product cost is increased.

There is a similar problem in a transmission mechanism of a power transmission device incorporating a multi-stage transmission, or in a control clutch for controlling a planetary gear employed as a center differential of a four-wheel drive vehicle.

In view of the above circumstances, the present invention provides a planetary gear type power transmission device which is easy to assemble and can reduce the width or length of the power transmission device without reducing durability and functionality. The purpose is to do.

[0017]

A first planetary gear type power transmission device according to the present invention comprises a planetary carrier supporting a planetary pinion of a planetary gear interposed in a power transmission system, and a power transmission member connected to the planetary carrier. And a drum having a friction engagement member for controlling the transfer of power to the drum via an operating member, wherein the planetary carrier is connected to the drum, and a load receiving surface formed on a side surface of the planetary carrier is further provided. The friction engagement member disposed on the inner periphery of the drum is provided facing a surface facing the operation member.

The second planetary gear type power transmission device comprises:
In the first planetary gear type power transmission device, notches are formed at set intervals at an open end of the drum, and a projection engaging with the notches is formed on the outer periphery of the planetary carrier. A pickup sensor is provided on the outer periphery of the carrier.

[0019] The third planetary gear type power transmission device comprises:
The first planetary gear type power transmission device is characterized in that the drum is formed by drawing, a trimming surface is set as a contact end surface with the planetary carrier, and the contact end surface is punched during trimming.

[0020] The fourth planetary gear type power transmission device comprises:
The first planetary gear type power transmission device is characterized in that the drum is formed by drawing, a trimming surface is set to a contact end surface with the planetary carrier, and coining forming is performed after trimming the contact end surface.

That is, in the first planetary gear type power transmission device, when an operation load is applied via an operation member to a friction engagement member which is provided in a power transmission system and controls transmission and reception of power to and from the power transmission member, The frictional engagement member receives the reaction force from the load receiving surface disposed on the side facing the frictional engagement member and performs the coupling operation. The load receiving surface is formed on a side surface of a planetary carrier that supports a planetary pinion of the planetary gear, and the planetary carrier is connected to a drum containing the friction engagement member, and an operating load applied to the friction engagement member Is supported by the entire planetary carrier.

According to a second planetary gear type power transmission device, in the first planetary gear type power transmission device, projections formed on the outer periphery of the planetary carrier are formed in notches formed at predetermined intervals in the opening end of the drum. By engaging the notch with the projection to rotate the drum and the planetary carrier together, and detecting the passage of the projection by a pickup sensor provided on the outer periphery of the planetary carrier, and passing the projection. The rotation speed and the like of the drum are calculated from the interval time and the like.

In a third planetary gear type power transmission device, in the first planetary gear type power transmission device, the drum is formed by drawing and a trimming surface is set to a contact end surface with the planetary carrier, and the contact end surface is set. Formed by punching during trimming.

[0024] The fourth planetary gear type power transmission device is as follows.
In the first planetary gear type power transmission device, the drum is formed by drawing and a trimming surface is set to a contact end surface with the planetary carrier, and the contact end surface is trimmed and coined to perform an end surface treatment.

[0025]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. 1 to 6 show a first embodiment of the present invention.

Reference numeral 21 in FIG. 1 denotes a power transmission device having a built-in continuously variable transmission 22 and a front / rear switching device 23 and a starting device 24 provided on the input side of the continuously variable transmission 22. An engine A is provided on the input side of the power transmission device 21.
Are connected.

The starting device 24 has the engine A
Fixing plate 25 connected to the crankshaft A1
A torque converter case 26 to which the clutch fixing plate 25 is fixed is connected to a pump impeller 27a of the torque converter 27. Further, a torque converter output shaft 28 extending from a turbine runner 27b connected to the pump impeller 27a via a fluid extends to the forward / reverse switching device 23 side.

The torque converter case 26 has a lock-up clutch 26 connected to the turbine runner 27b.
a is opposed. This lock-up clutch 26a
Is engaged with the torque converter case 26, the driving force of the engine A is transmitted directly to the pulley input shaft 33a of the continuously variable transmission 22 via the turbine runner 27b without passing through the torque converter 27, and is in a lock-up state. become.

A stator 27c for rectifying the fluid of the torque converter 27 is connected to a stator shaft 27e fixed directly or indirectly to the main body case 24a of the starting device 24 via a one-way clutch 27d. ing. Reference numeral 29 denotes the pump impeller 27.
This is an oil pump driven to rotate by a.

The forward / reverse switching device 23 is provided with a forward clutch 30, a planetary gear 31, and a reverse brake 32.
A torque converter output shaft 28 extending from the turbine runner 27b is connected to a clutch drum 30a provided on the forward clutch 30 and a clutch hub which is one of power transmission members provided on the forward clutch 30. 30b is connected to a pulley input shaft 33a extending from a primary pulley 33 provided on the continuously variable transmission 22, and furthermore, a shaft end 33 of the pulley input shaft 33a.
The sun gear 31a of the planetary gear 31 is integrally formed with the sun gear 31c.

The sun gear 3 of the planetary gear 31
A planetary carrier 31d that supports a planetary pinion 31c that connects the ring gear 1a and the ring gear 31b is connected to the clutch drum 30a of the forward clutch 30. Further, a reverse brake piston 32a provided on the reverse brake 32 is connected to the main body case 23a of the forward / reverse switching device 23 so as to be able to advance and retreat in a state where the rotation direction is restricted. When the ring gear 31b of the planetary gear 31 is fixed via the reverse brake 32 by the reverse brake piston 32a,
The planetary pinion 31c rotates, and the sun gear 31
The pulley input shaft 33a is rotated in reverse in a decelerated state via a.

Further, the primary pulley 33 of the continuously variable transmission 22 and a secondary pulley 34 provided opposite to the primary pulley 33 are connected via a belt 35, and a pulley for supporting the secondary pulley 34 is provided. The output shaft 34a is connected via a reduction gear group 15a of the final reduction device 35 to a differential device 35b which is mounted on a drive shaft 36 of a front wheel or a rear wheel.

In the continuously variable transmission 22, the pulley groove width is set by a primary hydraulic pressure supplied to a primary hydraulic chamber 33b provided in the primary pulley 33. The secondary hydraulic pressure supplied to the secondary hydraulic chamber 34b provided in the secondary pulley 34 applies a tension required for transmitting torque to the secondary pulley 34. The primary hydraulic pressure and the secondary hydraulic pressure are set by a transmission control device (not shown) based on the engine operating condition and the like. In the continuously variable transmission 22, the groove widths of both pulleys 33 and 34 are set in an inversely proportional state to achieve desired values. Get the reduction ratio.

As shown in FIG. 2, the shaft end 28a of the torque converter output shaft 28 extending from the turbine runner 27b of the torque converter 27 is connected to the shaft end 33c of the pulley input shaft 33a extending from the primary pulley 33. And is supported so as to be relatively rotatable. The base of the pulley input shaft 33a is supported by the main body case 23a of the forward / reverse switching device 23 via the bearing 17. An outer diameter of the sun gear 31a is formed to be slightly smaller than a base portion of the pulley input shaft 33a which is supported by the bearing 17, and the pulley input shaft 3 with respect to the bearing 17 is formed.
The press-fitting of 3a is facilitated.

Further, a concentric concave portion 30c is formed in the clutch drum 30a, and this concave portion 30c is formed on the outer periphery of a pump cover 23b of the oil pump 29 integrally formed with the main body case 24a of the torque converter 27. The input unit 30 is rotatably mounted via the input unit 30 and is formed at the center of rotation of the clutch drum 30a.
d is the torque converter output shaft 28 and the pulley input shaft 33a
, And is spline-engaged with the shaft end 28a of the torque converter output shaft 28. An output portion 30e formed in the direction of the center of rotation of the clutch hub 30b is engaged with a spline groove having a slightly smaller diameter at the shaft end 33c of the pulley input shaft 33a.

The clutch hub 30b and the clutch drum 30a are connected to each other via a multi-plate clutch 30f, which is a frictional engagement member. Of the multi-plate clutch 30f, and a retaining plate 30h is provided opposite the rear surface of the multi-plate clutch 30f. Further, a load receiving surface 31e formed on the side surface of the planetary carrier 31d is provided opposite to the rear surface of the retaining plate 30h, and the rear surface of the load receiving surface 31e is fitted to the opening end of the clutch drum 30a. Snap ring 30i.

The entire side surface of the retaining plate 30h is the load receiving surface 31e of the planetary carrier 31d.
Abuts on the snap ring 30i via the load receiving surface 31e.
h is reinforced, so that this retaining plate 30
h can be set to be relatively thinner than usual.

As shown in FIG. 4, the clutch drum 3
A spline groove 30j that engages with the drive plate of the multi-plate clutch 30f is formed in the opening end direction at 0a, and a cutout portion 30k is formed at the opening end continuous with the spline groove 30j. On the other hand, on the outer periphery of the planetary carrier 31d, a projection 31f engaging with the notch 30k is formed in a comb-like shape.

Further, as shown in FIG.
The main body is connected to the main body case 23 of the forward / reverse switching device 23.
The detection unit 37a of the pickup sensor 37 fixed to the position a is opposed to the detection unit 37a. The pickup sensor 37 is connected to a transmission control device (not shown) or an engine control device that controls a fuel injection pulse width, an ignition timing, and the like, and detects a magnetic field generated when a projection 31f formed on the outer periphery of the planetary carrier 31d passes. A signal generated by a change or the like is output.

Next, the operation of the embodiment having the above configuration will be described. In the assembling process of the power transmission device 21, the clutch hub 30 connected to the inner periphery of the clutch drum 30a of the forward clutch 30 via the multi-plate clutch 30f is connected.
b, the planetary carrier 3 of the planetary gear 31
1d is opposed to the planetary carrier 31d.
Are locked on the clutch drum 30a by the snap ring 30i, and the components constituting the forward clutch 30 are previously integrated with the clutch drum 30a and the planetary carrier 31d in a state where they are prevented from coming off. be able to. As a result, in the final assembly process, it is only necessary to mount the integrated forward clutch 30. Therefore, the work efficiency in the final process is improved, and the defective assembly rate is reduced, thereby improving the productivity. it can.

The power transmission device 21 that has been assembled in a predetermined manner is mounted on a vehicle together with the engine A integrated with the power transmission device 21, and when the engine A is started, the output of the engine A is changed to the crankshaft A1. The clutch drum 30a connected to the torque converter 27 provided in the starting device 24 via the torque converter 27 is connected to the torque converter output shaft 28 of the torque converter 27, and the planetary carrier 31d engaged with the clutch drum 30a is rotated.

A projection 31f is formed on the outer periphery of the planetary carrier 31d to engage with a notch 30k formed at the open end of the clutch drum 30a. A detection unit 37a of a fixed pickup sensor 37 is provided opposite to the pickup unit 37. The pickup sensor 37 detects a change in voltage when the protrusion 31f passes through the detection unit 37a, and detects a change in transmission voltage (not shown). Output to the control device and the engine control device. Then, the two control devices calculate the rotation speed of the torque converter output shaft 38 based on the detection signal from the pickup sensor 37.

When the engine is started and the select lever (not shown) is set in the N (neutral) range, both the forward clutch 30 and the reverse brake 32 of the forward / reverse switching device 23 are open. Therefore, the planetary gear 31 provided in the forward / reverse switching device 23 idles, and the continuously variable transmission 2
2 is interrupted.

When the select lever is set to a forward drive range such as a D (drive) range, the clutch piston 30g of the forward clutch 30 operates to apply an operating load to the multi-plate clutch 30f. The clutch 30f is brought into the connected state. The reverse brake 32 is kept open.

At this time, the operating load applied to the multiple disc clutch 30f is received by the entire load receiving surface 31e of the planetary carrier 31d via the retaining plate 30h. As a result, the retaining plate 30h is reinforced by the load receiving surface 31e, and the thickness of the retaining plate 30h can be relatively reduced. By reducing the thickness of the retaining plate 30h, The width or length W of the power transmission device 21 can be reduced.

When the multi-plate clutch 30f is engaged, the driving force from the turbine runner 27b of the torque converter 27 is applied to the clutch drum 30a provided on the forward clutch 30 of the forward / reverse switching device 23 via the torque converter output shaft 28. Multiple disc clutch 30f, clutch hub 30b
The pulley input shaft 33a of the primary pulley 33 provided in the continuously variable transmission 22 is rotated forward through the clutch hub 30b.

When the vehicle shifts to the steady running after the start, the lock-up clutch 26a provided on the start device 24 is engaged, and the clutch shaft A1 of the engine A is fixed to the fixed plate 2.
5. A lock-up state is established in which the lock-up clutch 26a and the turbine runner 27b of the torque converter 27 are directly connected to the torque converter output shaft 28.

On the other hand, when the driver sets the select lever to the R (reverse) range in order to travel backward, the reverse brake 32 is engaged and the forward clutch 30 is released. When the forward clutch 30 is disengaged, the clutch drum 30a and the clutch hub 30b are disengaged, and the reverse brake 32 is connected to the ring gear 31 of the planetary gear 31.
b is fixed, and the driving force transmitted from the torque converter output shaft 28 to the clutch drum 30a
The light is transmitted to the planetary pinion 31c via the planetary carrier 31d of the planetary gear 31 connected to the planetary gear 31a.

At this time, since the ring gear 31b is fixed by the reverse brake 32, the planetary pinion 31c supported by the planetary carrier 31d is rotated, and is transmitted to the continuously variable transmission 22 via the sun gear 31a. The provided pulley input shaft 33a is rotated reversely in a decelerated state.

In the present embodiment, the clutch drum 3
0a and the output portion 30e of the clutch hub 30b are disposed at positions substantially overlapping in the axial direction, and the load receiving surface 31e of the planetary carrier 31d is positioned between the retaining plate 30h and the snap ring 30i. By reducing the thickness of the retaining plate 30h, the width of the forward / reverse switching device 23 can be reduced, and therefore, the width or length W of the power transmission device 21 can be reduced. It is possible to easily mount the engine A and the power transmission device 21 integrated with the engine A in a horizontal state in a recent engine room which tends to be narrow. become.

Further, since the pulley input shaft 33a is directly supported by the main body case 23a via the bearing 39, the support accuracy of the primary pulley 33 is high, and high rigidity can be obtained. Further, since the outer diameter of the sun gear 31a is formed to be slightly smaller than the base of the pulley input shaft 33a which is supported by the bearing 39,
The pulley input shaft 33a can be easily pressed into the bearing 39 without damaging the sun gear 31a.

When the clutch drum 30a is formed by using a press machine or the like, generally, the cast material is plastically deformed through a plurality of drawing steps to finish it into a final product. In this case, as shown in FIG. 5, in a certain processing step, a pair of punches 42a and a die 42b for plastically deforming the shaped material 41 of the clutch drum 30a include:
A protrusion 43 for forming a portion to be the spline groove 30i and the notch 30k of the clutch drum 30a.
a, by forming the concave portion 43b in advance, it is possible to form the spline groove 30i and the cutout portion 30k at the same time in the drawing process, thereby reducing the number of processing steps. .

In this case, as shown by a broken line AA in the drawing, the trimming surface is positioned at a position where the projection 31f of the planetary carrier 31d engaged with the cutout portion 30k does not come into contact, that is, the trimming surface of this projection 31f. By setting the trimming surface in the middle of the rising surface oriented in the same direction as the extending direction, the trimming surface does not need to be post-processed, and the number of processing steps can be reduced accordingly.

As shown by the broken line in FIG. 6 (a), the cutout portion 30k of the clutch drum 30a of the semi-finished product 41, which is a semi-finished product that has been processed in a predetermined manner, is indicated by a broken line A-.
A, A'-A ', the planetary carrier 31 in the notch 30k
It is necessary to surface-treat the end surface 30m that contacts the projection 31f of d. In this case, as shown in FIG. 3B, in the trimming step, the inner and outer peripheries on the product side are sandwiched between a pair of dies 43a and 43b, and a punch 43c is used to punch out a portion to be the cutout portion 30k. Thereby, the surface treatment can be made unnecessary.

When the portion to be the cutout 30k is trimmed by a normal process, for example, as shown in FIG. 4C, the cutout 30k is formed by a pair of press dies 44a and 44b. The surface treatment is performed by adding a coining step of pressing or hitting the end face 30m of the planetary carrier 31d that contacts the projection 31f.

FIG. 7 shows a second embodiment of the present invention. As shown in the present embodiment, the specifications of the load receiving surface 31e of the planetary carrier 31d provided on the planetary gear 31 such as hardness, surface roughness, and cotton production are determined by retaining the operating load from the multi-plate clutch 30. When the plate is set to have almost the same specifications as the plate, the retaining plate used in the first embodiment can be omitted. By eliminating the retaining plate, the multiple disc clutch 30 can be shortened, and the product cost can be reduced by reducing the number of parts.

The snap ring 30i does not need to be engaged with the clutch drum 30a at the same position as the spline groove 30j into which the drive plate of the multi-plate clutch 30f engages, as shown in FIG. By slightly expanding the open end of the drum 30a and engaging the snap ring 30i with this portion, assembly becomes easy.

FIG. 9 shows a third embodiment of the present invention. In the present embodiment, a planetary carrier 53b that supports a planetary pinion 53a provided on a front planetary gear 53 of a compound planetary gear 52 employed in a transmission of a power transmission device 51, a clutch drum 54a provided on a forward clutch 54, At the binding site of
An example to which the present invention is applied will be described.

The compound planetary gear 52 is provided with a torque converter output shaft 55 extending from a torque converter (not shown).
And a transmission output shaft 56 connected to the drive shaft. The transmission output shaft 56 has a front planetary gear 53 and a rear planetary gear 57.
The open end of the planetary carrier 53b supporting the planetary pinion 53a
c overhangs and extends rearward. At the open end of the planetary carrier 53b, a load receiving surface 53d is formed in a flange shape, and projections 53e are formed on the outer edge of the load receiving surface 53d at regular intervals.

On the other hand, the clutch drum 54a includes a support member 51b fixed to the transmission case 51a.
And is rotatably supported, and has an open end extending forward. A clutch piston 54b is provided in the clutch drum 54a, and an operating load input surface of the multi-plate clutch 54c is provided opposite the clutch piston 54b. The multi-plate clutch 54c connects or releases the clutch drum 54a and a ring gear 57a, which is one of the power transmission members of the rear planetary gear 57. A retaining plate 54d is disposed on the back of the multi-plate clutch 54c. The planetary carrier 53b is provided on the back of the retaining plate 54d.
The load receiving surface 53d is formed opposite the load receiving surface 53d, and the back surface of the load receiving surface 53d is hooked on a snap ring 54e.

The multi-plate clutch 54c and the retaining plate 54d are engaged with spline grooves 54f formed on the inner periphery of the clutch drum 54a.
The projections 53e formed on the planetary carrier 53b are engaged with notches 54g formed at regular intervals at the opening end of the clutch drum 54a.

According to the present embodiment, when an operating load is applied to the multi-plate clutch 54c via the clutch piston 54b, the multi-plate clutch 54c is connected to the retaining plate 54d and the load receiving surface 53 of the planetary carrier 53b.
d, receiving the reaction force from the snap ring 54e and being joined.

At this time, the retaining plate 54
Since the entire back surface is supported by the load receiving surface 53d, the rigidity can be sufficiently ensured even if the thickness of the retaining plate 54d is reduced, and the thickness of the retaining plate 54d can be reduced. Thus, the cost of parts can be reduced, and the overall length of the power transmission device 51 can be reduced.

In this case, when the specifications such as the hardness, surface roughness, and degree of cotton of the load receiving surface 53d of the planetary carrier 53b are set to substantially the same specifications as those of the retaining plate 54d, The retaining plate 54d can be eliminated, and by eliminating the retaining plate 54d, the number of parts and the manufacturing cost can be reduced.

The present invention is not limited to the above embodiments. For example, the number of spline grooves formed in the clutch drum, the notch formed in the clutch drum, and the notch The projections formed on the outer periphery of the planetary carrier to be engaged do not necessarily need to coincide with each other, and the number of the notches and the projections may be larger or smaller than the number of spline grooves. Furthermore, the present invention is not limited to the above-described embodiments, as long as the planetary carrier that supports the planetary pinion of the planetary gear has a configuration that is coupled to the clutch drum of the clutch. May be a planetary gear type center differential that positively controls the pressure.

[0066]

As described above, according to the present invention,
Since the load receiving surface provided on the planetary carrier that supports the planetary pinion of the planetary gear is provided on the operating load receiving side of the frictional engagement member provided inside the drum, and the planetary carrier is hung on the drum, The operating load applied to the friction engagement member can be supported by the entire load receiving surface provided on the planetary carrier, so that the durability can be improved, and the friction engagement member such as a conventional retaining plate can be used. Reduce the thickness of the member that receives the operating load applied to the member, or make the hardness, surface roughness, surface accuracy, etc. of the load receiving surface almost the same as those of the member that receives the operating load, such as the retaining plate. When it is set to, it becomes possible to abolish this member itself, and accordingly, without reducing the functionality, the width of the power transmission device or Is not only can be shortened, it is possible to realize the efficient manufacturing and assembly by simplifying the structure.

[Brief description of the drawings]

FIG. 1 is a schematic diagram of a power transmission device according to a first embodiment.

FIG. 2 is a front sectional view of the forward / reverse switching device.

FIG. 3 is a sectional view of a main part showing a state in which a pickup sensor is provided in the forward / reverse switching device.

FIG. 4 is an exploded perspective view showing an assembled state of the clutch drum, the planetary carrier, and the snap ring.

FIG. 5 is a sectional view showing a state of forming the clutch drum;

FIG. 6 is a side sectional view showing a contact end surface treatment of the clutch drum;

FIG. 7 is a front sectional view corresponding to FIG. 2 according to a second embodiment;

FIG. 8 is a sectional view of a main part showing another embodiment of the present invention.

FIG. 9 is a side sectional view of a power transmission device incorporating a multi-stage transmission according to a third embodiment.

FIG. 10 is a front sectional view of a forward / reverse switching device according to a conventional example.

[Explanation of symbols]

21, 51 ... power transmission device 30a, 54a ... clutch drum 30b, 57a ... power transmission member (clutch hub, ring gear) 30f, 54c ... friction engagement member 30k, 54g ... notch 31, 31, ... planetary gear 31c, 53a ... Planetary pinion 31d, 53b Planetary carrier 31e, 53d Load receiving surface 31f, 53e Projection 37 Pickup sensor AA, A'-A '... Trimming surface

Claims (4)

[Claims] A planetary carrier supporting a planetary pinion of a planetary gear interposed in a power transmission system, and a friction engagement member connected to the planetary carrier and controlling transmission and reception of power to and from a power transmission member via an operating member. A planetary gear type power transmission device having an internal drum, wherein the planetary carrier is connected to the drum, and a load receiving surface formed on a side surface of the planetary carrier is disposed on an inner periphery of the drum. A planetary gear type power transmission device, which is provided on a surface of the member facing the operation member. 2. A notch is formed at an opening end of the drum at a predetermined interval, a projection engaging with the notch is formed on an outer periphery of the planetary carrier, and a pickup is formed on an outer periphery of the planetary carrier. The planetary gear type power transmission device according to claim 1, wherein a sensor is provided opposite to the power transmission device. 3. The planetary gear according to claim 1, wherein said drum is formed by drawing, a trimming surface is set as a contact end surface with said planetary carrier, and said contact end surface is punched out during trimming. Type power transmission device. 4. The planetary gear power according to claim 1, wherein said drum is formed by drawing, a trimming surface is set as a contact end surface with said planetary carrier, and said contact end surface is coined after trimming. Transmission device.