JPH0619191B2 - Cylinder of annular hydraulic servo - Google Patents

Description

The present invention relates to a cylinder of an annular hydraulic servo of an automatic transmission.

(Prior Art) In a conventional automatic transmission, each gear stage is formed by selectively engaging and disengaging elements such as gears and carriers of a plurality of planetary gear units, and each element is an oil pump. The discharge pressure from is adjusted by the hydraulic control device, and the hydraulic servo is operated by the control pressure,
By selectively engaging and disengaging the clutch, the brake and the like, the connection is made selectively, and friction engagement elements such as the clutch and the brake are provided in the transmission case.

In addition, in the four-wheel drive transfer, two-wheel drive and four-wheel drive
Friction engaging elements such as clutches and brakes are provided in the transfer case for switching the wheel drive.

When disposing a clutch as these friction engagement elements, a hydraulic servo is provided to disengage the clutch,
The hydraulic servo has a hydraulic cylinder composed of an outer cylinder portion, an inner cylinder portion, and an annular plate-like portion connecting the two, and a piston that slides inside the hydraulic cylinder.

FIG. 9 is a sectional view of a cylinder of a conventional annular hydraulic servo.

In the figure, a cylinder 200 of an annular hydraulic servo has an inner plate portion 201, an outer cylinder portion 203 having an inner spline 202 formed on its circumference, and an inner spline 204 having a rotary shaft slidably fitted therein. The inner cylinder portion 209 is formed with an oil passage hole 208 for supplying pressure oil to a hydraulic servo 207 configured together with the piston 206. From the oil passage hole 208, the hydraulic servo 207 is formed. The pressure oil can be supplied to and discharged from the clutch to disengage the clutch.

However, in the hydraulic servo of the automatic transmission, the hydraulic control device supplies the regulated hydraulic oil to engage and disengage the friction engagement element. As a result, the hydraulic pressure may decrease, and the pressure of the entire automatic transmission may decrease. Therefore, when processing the inner spline 202 of the outer cylinder portion 203,
It is necessary to form the relief portion 211 for preventing the gear cutting tool from interfering with the piston sliding portion, and the axial dimension of the outer cylinder portion 203 is correspondingly lengthened, which can reduce the size of the automatic transmission. Can not.

Further, the clutch disengaged by the annular hydraulic servo has to set the number of clutch plates and the spline tooth profile according to the transmission torque capacity thereof. However, in the cylinder 200 of the annular hydraulic servo, the outer cylinder portion 203 is used. Since the inner cylinder portion 209 is integrally formed, the entire cylinder 200 must be replaced in order to change the length or the spline tooth profile of the inner spline 202 of the outer cylinder portion 203 according to the setting of the number of clutch plates. Inevitably low productivity.

Therefore, the outer cylinder member having the inner spline and the annular plate member having the tubular portion are separately processed, and these are connected to form a cylinder to easily process the inner spline. An annular hydraulic servo cylinder has been provided to enable this (Actual Kosho 4
6-17854).

In this case, since it is not necessary to form a relief portion for processing the inner spline, the axial dimension corresponding to the relief portion can be shortened.

(Problems to be solved by the invention) However, in the above-described conventional annular hydraulic servo cylinder, the outer cylinder member and the annular plate member are spline-fitted, and a snap ring is attached to fix the both. Therefore, it is necessary to provide a space for mounting the snap ring on the outer cylinder member, which increases the axial dimension of the outer cylinder member.

In addition, since it is necessary to form a spline for spline fitting with the outer cylinder member in the tubular portion of the annular plate member, the tubular portion becomes thick, and the inner cylinder of the outer cylinder member is The inner diameter of the tubular portion becomes smaller. Therefore, the outer diameter of the piston cannot be increased and the clutch capacity is reduced. That is, in order to secure the predetermined clutch capacity, the cylinder of the annular hydraulic servo must be enlarged.

An object of the present invention is to provide a cylinder of an annular hydraulic servo which can solve the problems of the conventional cylinder of the annular hydraulic servo and can be downsized while ensuring the capacity of the friction engagement element. To do.

(Means for Solving the Problems) In order to achieve the above object, the present invention forms an oil pressure servo with a piston, an outer cylinder member having an inner peripheral spline formed, and an oil for supplying hydraulic oil to the oil pressure servo. In an annular hydraulic servo cylinder comprising an inner cylinder member having a passage hole, an outer cylinder member and an inner cylinder member, which are formed separately from each other, and an annular plate member connecting them, the inner cylinder member is a shaft. It has an oil passage provided almost perpendicular to the direction and also has an annular welding stop projection, and the annular plate member abuts the circumference on the welding stop projection of the inner cylinder member and is fixed by welding. And has a cylindrical portion on the outer periphery, and the outer peripheral cylindrical surface of the cylindrical portion is fitted to the inner peripheral cylindrical surface portion of the outer cylinder member. The outer cylinder member on the side opposite to the end is fixed by welding.

(Operation and Effect of the Invention) According to the present invention, the outer cylinder member in which the inner peripheral spline is formed as described above and the annular plate member that connects the outer cylinder member and the inner cylinder member are separately formed. Therefore, it is not necessary to form a relief portion for cutting the inner spline on the outer cylinder member, so that the axial dimension of the outer cylinder member is shortened and the cylinder of the annular hydraulic servo can be made compact. it can.

Furthermore, since the inner cylinder member and the annular plate member are formed separately, the oil passage hole formed in the inner cylinder member can be formed perpendicularly to the axial direction, and as a result, the inner diameter of the piston The side sliding portion can be formed in the vicinity of the annular plate member. Therefore, a sufficient piston stroke can be secured and the axial dimension of the inner cylinder member can be shortened. The inner cylinder member has a cylindrical portion on the outer circumference, and the inner peripheral cylindrical surface of the outer cylinder member and the outer peripheral cylindrical surface of the cylindrical portion of the annular plate member are fitted together and fixed by welding. Since it is not necessary to provide a locking portion such as a snap ring, the axial dimension can be shortened.

Furthermore, since the outer cylinder member and the tubular portion of the annular plate member are connected by welding, they can be fitted to each other on their cylindrical surfaces, which not only facilitates the working of the fitting portion, but also The rigidity of the welded portion can be increased. Moreover,
The wall thickness of the cylindrical portion of the cylindrical member can be reduced, and the outer shape of the piston can be increased correspondingly to obtain a large clutch capacity.

Further, since the outer cylinder member is configured separately, it is not necessary to replace the entire cylinder in order to change the length and tooth profile of the inner spline of the outer cylinder member according to the setting of the number of clutch plates.

Further, when the outer cylinder member, the inner cylinder member and the annular plate member are formed separately, the concentricity of the piston sliding part, that is, the concentricity of the outer cylinder member and the inner cylinder member becomes a problem. The circumferential cylindrical surface of the member and the outer circumferential cylindrical surface of the tubular portion of the annular plate member are fitted and fixed by welding, and the circumference of the annular plate member is fixed to the annular welding stop projection of the inner cylinder member. Since they are in contact with and fixed by welding, the concentricity of the piston sliding portion is secured.

(Example) Hereinafter, the Example of this invention is described in detail, referring drawings.

FIG. 2 is a sectional view of a four-wheel drive transfer incorporating a cylinder of an annular hydraulic servo according to the present invention, and FIG. 3 is a main sectional view thereof.

The transfer 100 is provided in the transfer case 2, and is a hydraulic multi-plate friction engagement clutch for shifting (hereinafter abbreviated as a shift clutch) C3, which is a friction engagement element, and a hydraulic multi-plate friction engagement brake (hereinafter abbreviated as a brake) C3. ) B4 and 2
A four-wheel drive four-wheel drive switching hydraulic multi-plate friction engagement clutch (hereinafter abbreviated as two-wheel four-wheel switching clutch) C4 and a planetary gear set (not shown) of a main transmission including an automatic transmission in a transmission case. Set the output shaft 132 to the input shaft (13
2), the first output shaft 142 of the transfer 100 arranged in series with the input shaft (132), the input shaft (132) and the first output shaft 142.
Planetary gear set P arranged between the output shaft 142
f, a four-wheel drive sleeve 151 rotatably fitted over the first output shaft 142, and mounted in the opposite direction to the first output shaft 142 arranged in parallel with the input shaft (132). It has a second output shaft 152 and a transmission mechanism 153 between the sleeve 151 and the second output shaft 152.

The speed change clutch C3 is disposed on the transmission case side of the planetary gear set Pf, and connects and disconnects the sun gear S1 and the carrier P1. The speed change clutch C3 is connected to the carrier P1. When the shift lever of the transmission is selected to the parking position, the pawl 31b meshes with the parking gear 31a, and the hydraulic servo C is composed of the cylinder 3 for fixing the first output shaft 142 and the piston 3P mounted in the cylinder 3. −
Operated by 3.

The planetary gear set Pf is a sun gear S1 spline-fitted to the end of the input shaft (132) of the transfer 100,
The planetary pinion P meshing with the sun gear S1, the ring gear R1 meshing with the planetary pinion P, and the planetary pinion P are rotatably held and connected to the tip of the first output shaft 142 of the transfer 100. It consists of carrier P1.

Brake B4 is ring gear R1 transfer case 2
Is a hydraulic multi-plate friction engagement brake for fixing to a cylinder, and is operated by a hydraulic servo B-4 composed of a cylinder 4 formed in the transfer case 2 and a piston 4P mounted in the cylinder 4. It

The two-wheel / four-wheel switching clutch C4 connects and disconnects the first output shaft 142 of the transfer 100 connected to the carrier P1 and the sleeve 151 connected to one sprocket 156 of the transmission mechanism 153 for driving the second output shaft 152. Is a hydraulic multi-plate friction engagement clutch for operating by a hydraulic servo C-4 composed of a cylinder 5 rotatably supported by the transfer case 2 and a piston 5P mounted in the cylinder 5. .

The cylinder 5 of the hydraulic servo C-4, which is the cylinder of the annular hydraulic servo of the present invention, has an outer circumference 51 as shown in FIGS.
A ring-shaped plate member 53 obtained by press-molding a tubular portion 52 on the inner surface of the tubular member 5 and an inner circumference 54a at one end thereof are formed on the tubular portion 5 as shown in FIGS.
2 is externally fitted, and after press-fitting the tubular portion 52, the entire circumference is welded,
2 on the inner spline 541 formed on the other inner circumference 54b
The outer cylinder portion 54 spline-fitted to the clutch plate 50A of the four-wheel four-wheel switching clutch C4, and the first, fifth, and sixth cylinders.
As shown in the figure, the annular plate member 53 and the annular plate member 53
Is set at a predetermined position, and is welded at one end 55 having a welding stop convex portion 55a which makes it easy to secure concentricity at the time of welding. A flange plate groove 57a for fixing the flange plate 572 supporting the return spring 571 of −4 is formed, and is bent in the radial direction from the vicinity of the flange plate groove 57a and the axial oil passage 57b is formed.
Is formed, is bent in the axial direction from the axial oil passage 57b, is fixed to the first output shaft 142 by snap rings 58a, 58b, and is rotated integrally with the first output shaft 142.
Inner spline that fits on 42 outer spline 142a
And an inner cylinder portion 59 forming 58.

The oil tightness (sealability) of the hydraulic servo C-4 on the outer peripheral side is ensured by the tubular portion 52 of the annular plate member 53, so that if the welded portion 50 has strength for transmitting torque. Good, several places on the lap.

In this way, the cylinder 5 of the hydraulic servo C-4 has an inner circumference 54
The outer cylinder portion 54 in which the inner spline 541 is formed on b, and the inner cylinder portion 5 connected to the first output shaft 142.
9, the outer cylinder part 54 and the inner cylinder part 5
It is composed of an annular plate member 53 connecting with the outer ring member 9, and the annular plate member 53 is formed separately from the outer cylinder portion 54.

Therefore, when the number of clutch plates or the spline tooth profile of the two-wheel / four-wheel switching clutch C4 is changed, it can be dealt with only by changing the outer cylinder portion 54. Ring plate member
The cost can be reduced because the 53 and the inner cylinder part 59 can be used together.

Further, since it is not necessary to form a relief portion for cutting the inner spline 541 in the outer cylinder portion 54,
Not only the cylinder 5 of the hydraulic servo C-4 can be made compact by shortening the axial dimension of the outer cylinder portion 54, but also the machining for the radial oil passage hole 56 of the inner cylinder portion 59 is performed in the axial direction. And vertical direction (radial direction)
Therefore, the axial dimension of the inner cylinder portion 59 can be shortened and the working operation can be facilitated.

Further, the inner cylinder part 59 has a cylindrical part 52 on the outer circumference, and the cylindrical surface of the inner circumference 54a of the outer cylinder part 54 and the cylindrical surface of the outer circumference 51 of the cylindrical part 52 of the annular plate member 53. Are fitted and fixed by welding.

Therefore, it is not necessary to provide a locking portion such as a snap ring, and the axial dimension can be shortened.

Further, since the outer cylinder portion 54 and the tubular portion 52 of the annular plate-shaped member 53 are fixed by welding, both can be fitted to each other at their cylindrical surfaces, and the fitting portion can be easily processed. Not only that, the rigidity of the welded portion 50 can be increased. Moreover, the thickness of the tubular portion 52 of the annular plate member 53 can be reduced, and the outer diameter of the piston 5P can be correspondingly increased to obtain a large clutch capacity.

Furthermore, the welded portion between the outer cylinder portion 54 and the tubular portion 52.
Since 50 is the end of the outer cylinder part 54 on the side opposite to the tip of the tubular part 52, the welded part 50 is located away from the inner spline 541 of the outer cylinder part 54, and the inner spline caused by the heat of welding is used. The deformation of the 541 can be prevented, and distortion is unlikely to occur.

Moreover, since the wall thickness of the tubular portion 52 of the annular plate member 53 can be reduced, the annular plate portion 53 can be manufactured by press molding a thin plate material. In that case, not only the cost of the cylinder 5 of the hydraulic servo C-4 can be reduced, but also the weight and the size can be reduced.

When the annular plate member 53 is formed by press molding, since the wall thickness of the tubular portion 52 is reduced, it is possible to reduce the arc of the bent portion of the annular plate member 53 in the vicinity of the welded portion 50. . Therefore, by making the welded portion 50 near the outer periphery of the flange portion of the annular plate member 53 and extending and fitting the cylindrical surface of the outer cylinder portion 54 to the welded portion 50, welding can be further facilitated. .

Further, since the fitting portion is a cylindrical surface, the entire circumference of the tubular portion 52 can be easily welded.

The transmission mechanism 153 includes a sprocket 156 spline-fitted to the sleeve 151, a sprocket 155 formed on the second output shaft 152, and a chain 157 stretched between the sprocket spaces 155 and 156.

160 is a speed change clutch C3 of the transfer 100, a two-wheel / four-wheel switching clutch C4 and a hydraulic servo C-3 of a brake B4,
A transfer valve body provided with a transfer control device 163 for supplying and discharging hydraulic pressure to C-4 and B-4, 161
Is the oil pan. Hydraulic clutch C3 for speed change clutch C3, two-wheel / four-wheel switching clutch C4 and brake B4
The line pressure oil supplied to 3, C-4 and B-4 is guided to a transfer valve body 160 provided with a transfer control device 163 via an oil passage 164 provided in the transmission case and the transfer case 2. .

During normal running, the oil pressure servo C-3 is supplied with the line pressure supplied to the hydraulic control device of the automatic transmission through the oil passage 165 to engage the speed change clutch C3, and the hydraulic servos B-4 and C-4 are engaged. Is released to release the brake B4 and the two-wheel / four-wheel switching clutch C4. As a result, the sun gear S1 of the planetary gear set Pf and the carrier P1 are connected, the power is transmitted from the input shaft (132) to the first output shaft 142 at a reduction ratio of 1, and two-wheel drive traveling with only the rear wheels is obtained. At this time, the power from the input shaft (132) is transmitted from the carrier P1 to the first output shaft 142 via the speed change clutch C3 without passing through the sun gear S1, the planetary pinion P, and the ring gear R1. The surface is not loaded and the life of the gear is increased. During this two-wheel drive traveling, when four-wheel drive traveling becomes necessary, the shift lever (not shown) provided in the driver's seat or the like is manually shifted to apply the line pressure to the hydraulic servo C-4 of the transfer control device 163. When gradually supplied to smoothly engage the two-wheel / four-wheel switching clutch C4, the first output shaft 142 and the sleeve 151 are connected, and the transmission mechanism 153 and the second output shaft 15 are connected.
The power is also transmitted to the front wheels via 2 and a propeller shaft (not shown), and the power is transmitted from the input shaft (132) to the first output shaft 142 and the second output shaft 152 at a reduction ratio of 1.
A wheel-drive direct-connection running state (high-speed four-wheel drive state) can be obtained.
If the shift lever is manually shifted when it is necessary to increase the output torque such as on a steep slope during this four-wheel drive, the hydraulic pressure to the hydraulic servo is gradually supplied to the hydraulic servo B-4 at a proper timing. The hydraulic pressure of the hydraulic servo C-3 is discharged, the brake B4 is gradually engaged, and the shift clutch C3 is smoothly released. As a result, the sun gear S1 and the carrier P1 are released and the ring gear R1 is fixed, and power is transmitted from the input shaft (132) to the sun gear S1.
1, the planetary pinion P, and the carrier P1 are decelerated and transmitted to the first output shaft 142 and the second output shaft 152,
4-wheel drive running state with large torque (low-speed 4-wheel drive state)
Is obtained. Table 1 shows the manual shift setting range of the transfer 100, the brake B4, the speed change clutch C3, and the two wheels 4
The engagement and disengagement of the wheel switching clutch C4 and the running state of the vehicle are shown.

In Table 1, ∘ indicates the engaged state of the friction engagement element, and x indicates the released state. The reduction ratio (3.0 in the example) is calculated by setting the tooth ratio of the sun gear S1 and the ring gear R1 of the planetary gear set to λ.
And the gear ratio λ is 0.5, the reduction ratio = (1 + λ)
/ = Calculated with 3.0.

[Brief description of drawings]

FIG. 1 is a sectional view of a cylinder of an annular hydraulic servo of the present invention, and FIG. 2 is a sectional view of a cylinder of the annular hydraulic servo of the present invention.
Sectional view incorporated in a wheel drive transfer, Fig. 3 shows second
FIG. 4 is a main sectional view of the drawing, FIG. 4 is a sectional view of an annular plate member of the cylinder of the annular hydraulic servo of the present invention, and FIG. 5 is a sectional view of an inner cylinder portion of the cylinder of the annular hydraulic servo of the present invention. FIG. 6 is a front view of FIG. 5, FIG. 7 is a front view of an outer cylinder part of a cylinder of an annular hydraulic servo according to the present invention, FIG. 8 is a sectional view of FIG. 7, and FIG. It is sectional drawing of the cylinder of a hydraulic servo. 2 in the figure: transfer case, B4: brake, C
3 ... shift clutch, C4 ... two-wheel / four-wheel switching clutch,
B-4, C-3, C-4 ... hydraulic servo 5 ... cylinder, 53 ... annular plate member, 54 ... outer cylinder part, 56 ... radial oil passage hole, 59 ...
Inner cylinder part

 ─────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Kazuaki Watanabe 1 Toyota Town, Toyota City, Aichi Prefecture, Toyota Motor Co., Ltd. (72) Inventor Yoshiharu Harada, 1 Toyota Town, Toyota City, Aichi Toyota Motor Co., Ltd. (56) References JP-A-53-64144 (JP, A)

Claims (2)

[Claims] 1. An outer cylinder member forming a hydraulic servo with a piston and having an inner peripheral spline, an inner cylinder member having an oil passage hole for supplying hydraulic oil to the hydraulic servo, the outer cylinder member and the inner cylinder member. In a cylinder of an annular hydraulic servo, which comprises a cylinder member and an annular plate-shaped member that connects the two separately formed, the inner cylinder member has an oil passage provided substantially perpendicular to the axial direction, and Having an annular welding stop projection, the annular plate-shaped member abuts the inner periphery of the annular welding stop projection of the inner cylinder member, is fixed by welding, and has a tubular portion on the outer periphery. Then, the outer peripheral cylindrical surface of the tubular portion is fitted to the inner peripheral cylindrical surface portion of the outer cylinder member,
An annular hydraulic servo cylinder characterized in that the end of the outer cylinder member on the side opposite to the tip of the tubular part is fixed by welding. 2. The cylinder of an annular hydraulic servo according to claim 1, wherein the annular plate member is formed by pressing a thin plate material.