JPS6148644A - Lubrication mechanism of cylindrical rotary supporting section - Google Patents

Abstract

PURPOSE:To prevent a seal ring and a cylindrical bush from wearing by providing a lubrication oil hole in the clearance formed by a cylindrical rotary body, a rotary supporting section, a seal ring, and the cylindrical bush and also by providing spiral groove on the cylindrical bush. CONSTITUTION:Between a cylindrical rotary body 1 and thin cylindrical section 8E, a cylindrical bush 9 on which a groove 9A for feeding out lubrication oil backward is formed is provided. And a clearance B is formed by the inner circumference of the cylindrical rotary body, the outer circumference of a rotary supporting section 2, the rear face of a step 8D, a backward seal ring 5B, and the front face of the cylindrical bush 9. The clearance B is provided with the lubrication oil hole connected with a lubrication oil supply path 3C through a hole 8G provided to the sleeve 8 corresponding to the clearance B and a lubrication oil hole 2A provided to the rotary supporting section 2 corresponding to the hole 8G.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application 1] The present invention relates to lubrication between a cylindrical rotating body in an automatic transmission and a rotating support portion that supports the rotating body.

[Prior Art] Conventionally, the sealing and cylindrical bushings arranged between a cylindrical rotating body and a support part that supports the rotating body are lubricated by lubricating oil passing through the surfaces of each member. They were getting supplies.

[Problems to be solved by the invention] However, with conventional seal rings and cylindrical bushings, there was a risk that the lubricating oil supply would be insufficient when the vehicle was tilted or when traveling at high speeds, and durability would be impaired due to friction. . In addition, in recent years, attention has been paid to Teflon (tetrafluoroethylene resin, trade name), which has a smaller coefficient of friction than metals such as iron, for seal rings. If it is used between the rotating body and the support part in an automatic transmission that does not have a

An object of the present invention is to form a gap between a cylindrical rotating body, a rotating support part, a seal ring, and a cylindrical bushing, provide a lubricating oil hole in the gap through which an oil passage in the support part flows, and provide a lubricating oil hole between the cylindrical bushing and the cylindrical rotating body. By providing a groove through which lubricating oil flows in the cylindrical direction, the seal ring and cylindrical bushing are forcibly lubricated to prevent wear due to friction between the seal ring and cylindrical bushing. The present invention provides a lubrication mechanism for a cylindrical rotation support part that supplies lubricating oil to a lubricated member through a groove provided in a cylindrical bush.

[Means for Solving the Problems] In order to solve the above problems, a lubrication mechanism for a cylindrical rotating support part of the present invention includes a cylindrical rotating body, a lubrication mechanism disposed on the inner periphery of the cylindrical rotating body, and a lubrication mechanism for a cylindrical rotating support part. A cylindrical body comprising a rotary support part that supports the cylindrical rotary body by disposing a seal ring and a cylindrical bush between the rotating body and a support part support having an oil passage through which lubricating oil flows inside. In the rotating body support mechanism, the cylindrical rotating body,
A gap is formed between the rotation support part, the seal ring, and the cylindrical bushing, and a lubricant hole is provided in the gap through which an oil passage in the support part flows, and the lubricant oil flows in the cylindrical direction of the cylindrical bush. The configuration is such that a groove is provided.

[Operation and Effects of the Invention] The lubrication mechanism for the cylindrical rotating support part of the present invention having the above configuration forms a gap between the cylindrical rotating body, the rotation support part, the seal ring, and the cylindrical bushing, and the By providing a lubricating oil hole through which an oil passage flows in the part support, and providing a groove through which lubricating oil flows in the cylindrical direction of the cylindrical bushing, the seal ring and cylindrical bushing are forcibly lubricated, and the seal ring and cylindrical bushing are In addition to improving durability, lubricating oil can be supplied to the lubricated member on the opposite side of the gap between the cylindrical bushings through the groove provided in the cylindrical bushing.

(Effects of Example) By using Teflon (Teflon, a mixture of Teflon and carbon, etc.) for the seal ring, the durability of the seal ring is improved, the oil sealing property is improved, the weight of the seal ring is reduced, and the rotating body is This allows the use of a member that is weaker than a metal seal ring, and has the effect of allowing the rotating body to rotate more smoothly due to the lower friction coefficient of the seal ring.

[Example] Next, a lubrication mechanism for a cylindrical rotation support portion of the present invention will be described based on an example (not shown).

FIG. 1 is a sectional view showing a lubrication mechanism for a cylindrical rotation support according to the present invention, and FIGS. The figure and the hydraulic circuit of its hydraulic control circuit are shown.

Automatic transmission 100 includes a hydraulic torque converter 200, a transmission 300, and a hydraulic control device 400.

The transmission 300 includes a first planetary gear device UO1
One multi-plate tarlatch C01 operated by hydraulic servo
A--bird drive transmission 300A comprising one multi-disc brake BO1 and one one-way latch FO;
2nd planetary gear device U1, 3rd M star gear device U2. Two multi-disc clutches C1, C2, operated by hydraulic revo
One belt brake B1. Two multi-disc brakes B2
, B3, and two one-way latches F1 and F2, an underdrive transmission Uj3o with three forward speeds and one reverse speed.
It consists of oB etc.

A transmission case 110 of the automatic transmission 100 includes a torque converter housing 1 that accommodates a torque converter 200.
20. A transmission case 130 integrally formed with each chamber housing the overdrive transmission 300A and the underdrive transmission 300B, and the outer tension housing 140 that covers the rear side of the automatic transmission 100. The torque converter housing 120, the Heheras mission case 13, and the extensicon housing 140 are each fastened with a large number of bolts.

The torque converter 200 is housed in a torque converter housing 120 that is open at the front (engine side), and includes a front cover 201 that rotates under the drive of an engine (not shown), and an annular plate welded to the inner circumference of the front cover 201. A rear cover 202 having a shape, a pump impeller 203 disposed around the inner peripheral wall of the rear cover 202, a turbine launch 204 disposed opposite to the pump impeller 203, and a turbine shell 205 holding the turbine runner 204. , the stator 20 is supported by a fixed shaft 207 connected to the transmission case 110 via a one-way clutch 206, and increases the torque capacity when the input rotation speed is low.
8. The front cover 201 and the turbine shell 205
between the front cover 201 and the turbine shell 205
A lock-up clutch 209 is provided to ensure that the two rotate at the same time. An internal gear oil pump 150 having an external gear 150a and an internal gear 150b is housed between the cylindrical transmission case 130 and the torque converter housing 120, which are continuous to the rear of the torque converter housing 120. Oil pump body 15 having a cylindrical portion 151 protruding forward on the inner periphery
2 is fastened to the front part of the T-transmission engine case 130, and an extension member 210 connected to the inner circumferential end of the rear cover 202 extends through the inner circumference of the cylindrical part 151 to the external gear 150a.
It is spline fitted to the inner periphery of. Further, an oil pump cover 154 having a cylindrical front support 153 that is coaxial with the cylindrical portion 151 and protrudes rearward is fastened to the rear side of the oil pump body 152 to connect the oil pump housing 152 and the oil pump. cover 154
forms a partition between the torque converter housing 120 and the transmission case 130. Further, in the middle of the transmission case 130, there is a cylindrical wall projecting rearward that partitions an overdrive mechanism chamber 130A in which an overdrive transmission 300A is formed and an underdrive mechanism chamber 130B in which an underdrive transmission 300B is formed. A support support having a rotational support 2 is provided.

A rear support wall 134 having a cylindrical rear support 133 projecting forward is provided at the rear (right side in the figure) of the transmission case 130.

Inside the front support 153 is a one-sided clutch 2 that supports the stator 208 of the torque converter 200.
A fixed shaft 207 of No. 06 is fitted, and the input shaft 10 of the transmission 300, which is the output shaft of the torque converter 200, is rotatably supported inside the fixed shaft 207. The automatic transmission 100 of this embodiment receives power transmission that rotates clockwise from a viewpoint from the power input direction (engine side). The input shaft 10 has a flange portion 101 at the rear end.
A rearward facing hole 102 is formed in the center of the rear end. An intermediate power transmission shaft 11 arranged in series with the input shaft 10 is rotatably mounted behind the input shaft 10, and the tip of the intermediate power transmission shaft 11 slides into a hole 102 of the input shaft 10. , a flange portion 11 is provided at the rear end of the intermediate transmission shaft 11.
1, and an output shaft 12 that transmits power to the driving wheels at the center.
A rearward facing hole 112 is formed into which the tip of the holder slides.

The output shaft 12 has a sensor rotor 121 for detecting the rotation speed and a speedometer drive gear 122 fixed in the extension housing 140, and the rear end is splined on the outer periphery to fit a sleeve yoke that transmits power to the drive wheels. A groove 123 is formed therein, and the sleeve yoke is rotatably supported by the extension housing 140 via the sleeve yoke, and the front end is rotatably supported within the hole 112 of the intermediate transmission shaft 11 .

The overdrive transmission 300A has the input shaft 10
A first planetary gear unit UO is provided behind the , the ring gear RO is coupled to the intermediate transmission shaft 11 via a flange plate 113, the planetary carrier PO is coupled to the flange portion 101 of the input shaft 10, and the sun gear SO is It is formed by an inner race shaft 13 of a one-way latch FO.

On the front side of the first planetary gear unit UO, there is a first
The hydraulic servo drum 14 is fixed to the inner race shaft 13, and the annular piston 15 is fitted between the outer circumferential wall 14A and the inner circumferential wall 14B of the first hydraulic servo drum 14, so that the carrier PO and the first hydraulic servo drum 14 are engaged and A return spring 16 that forms the hydraulic servo C-0 of the clutch CO that releases the clutch CO and presses the annular piston 15 toward the inner race shaft 13 toward the hydraulic servo C-0, and an outer peripheral wall 1.
A clutch CO is installed on the inside of the clutch CO
The first hydraulic servo drum 14 and the inner race shaft 13 are connected to the carrier PO. A one-way latch FO with the inner race shaft 13 as an inner race is provided on the inner periphery of the first hydraulic servo drum 14, and an outer race 17 and a transmission case 1 are provided on the outer periphery of the one-way latch FO.
A clutch CO and a brake BO are provided between the piston 18 and the piston 18 that presses the brake BO in front of the rear support of the brake BO.
The hydraulic servo B- of the brake BO is located between the
0, and a return spring 19 that presses the piston 18 toward the hydraulic servo B-0 side is fitted into the inner peripheral portion 135 of the front end of the support. The second opening
A hydraulic servo drum 20 is rotatably fitted around the outer periphery of the rotary support part 2 of the support support, and a clutch C2 is installed between the outer peripheral wall 208 and the cylindrical rotating body 1, which is the inner peripheral wall of the present invention.
An annular piston 21 that presses the clutch C2 is fitted between the annular piston 21 and the second hydraulic servo drum 20.
The return spring 22 that forms the hydraulic servo C-2 and presses the annular piston 21 toward the inner peripheral wall 20B toward the hydraulic servo C-2, and the outer peripheral wall? Clutch C on the inside to 〇
2 is installed. Behind the second hydraulic servo drum 20, a third hydraulic servo drum 24, which is open to the rear and has an annular protrusion 23 to the right of the front, is fixed to the outer periphery of the flange portion 111 at the rear of the intermediate transmission shaft 11. The rear end of the shaft 11 and the outer peripheral wall 2 of the third hydraulic servo drum 24
An annular piston 25 that presses the clutch C1 is fitted between the outer periphery of the flange portion 111, forming a hydraulic servo C-1 of the clutch C1 between the annular piston 25 and the third hydraulic servo drum 24, and also forms a hydraulic servo C-1 of the clutch C1. A return spring 26 that presses the annular piston 25 toward the hydraulic servo C-1 side is attached to the circumferential side, and a clutch C2 is attached to the outer periphery of the annular projection 23.
Three hydraulic servo drums 20, 24 are connected. A second planetary gear arrangement U1 is provided behind the third hydraulic servo drum 24, and its ring gear R1 is connected to the ring gear R.
The carrier P1 is connected to the third hydraulic servo drum 24 via a clutch C1 and an annular protrusion 28 protruding in front of a rotary support member 27 that rotatably supports the carrier P1 on the outer periphery of the output shaft 12. is spline-fitted to the front outer periphery of the output shaft 12, and the Zang gear S1 is rotatably provided on the outer periphery of the output shaft 12. Hydraulic servo drum 2o,
24 and the second planetary gear unit U1 in a minimum space, the connecting drum 30 is fixed to the outer periphery of the second hydraulic first nerbo drum 20 at its front end, and the rear end is
A belt brake B1 that is connected to the first non-gear shaft 29 behind the second yIi star gear device U1 and fixes and releases the connecting drum 30 is provided on the outer peripheral side.

Also, inside the center the boat 4 (as shown in Fig. 3), there is a C-1 hydraulic oil supply passage 3A that communicates with the hydraulic servo C-1 and supplies and discharges hydraulic oil to the clutch C1, and a hydraulic oil passage 3A for the clutch C2. A C-2 hydraulic oil supply passage 3B that communicates with the servo C-2 and supplies and discharges hydraulic oil, a lubricating oil supply passage 3C that supplies lubricating oil from the outer circumference of the intermediate transmission shaft 11 to the inner circumference, and the brake. B.O.
B- communicates with the hydraulic servo B-0 and supplies and discharges hydraulic oil.
o A hydraulic oil supply oil passage 3D is provided.

The cylindrical rotating body 1 on the inner periphery of the second hydraulic servo drum 20 provided on the outer periphery of the rotational support part 2 of the support part support 4 is provided with (, -2 actuation) in the support part support 1 to 4. A hole 1A is provided (pulled) to communicate with the oil supply oil passage 3B, and the cylindrical rotating body 1
An oil groove 8A corresponding to the hole 1A is provided between the support portion 2 and the oil groove 8A, and seal ring grooves 8B and 8C are provided on the outer periphery on both sides of the oil groove 8A, and a thin cylindrical portion 8E is provided at the rear via a step 8D. The sleeve 8 is fixed to the outer periphery of the rotary support portion 2, and the oil groove 8A communicates with the C-2 hydraulic oil supply passage 3B via a hole 8F. The seal rings @8B and 6C of the sleeve 8 are provided with a front seal ring 5A and a rear seal ring 5B made of Teflon so as not to leak the hydraulic oil supplied to the hole 1A through the hole 9F and the oil groove 8A. There is. Further, a ring-shaped metal bearing 4A is disposed between the rear surface of the support part support 4 and the second hydraulic servo drum 20, and the second
A gap is formed between the hydraulic servo drum 20, the support 4, the metal bearing 4A, and the front seal ring 5A, and the gap A communicates with the C-2 hydraulic oil supply passage 3B through the seal ring lubricating oil hole 6. has been done. At the rear of the thin cylindrical portion 8F is a bearing 11 disposed between the rear end of the rotation support portion 2 and the front side of the seventh flange 111 of the intermediate transmission shaft 11.
It is provided longer than the rotation support part 2 so that the thrust race 113A on the front side of No. 3 can be fitted therein. Further, as shown in FIG. 4, the cylindrical rotating body 1 and the thin cylindrical portion 8E communicate with each other in the same direction, front and rear, on the inner circumferential side, so that the cylindrical rotating body 1 receives power transmission. A cylindrical bush 9 having an FI 9A is disposed so as to send lubricating oil to an object to be lubricated such as a washer 113C disposed at the rear by rotating in the same direction as the intermediate transmission shaft 11. The inner periphery of the rotating body 1, the outer periphery of the rotation support part 2, the rear surface of the stage 8D, and the rear seal ring 5B
A gap B is formed between the front surface of the cylindrical bushing 9 and the front surface of the cylindrical bushing 9. The gap B communicates with the lubricating oil supply oil path 3C via a hole 8G provided in the sleeve 8 corresponding to the gap B and a lubricating oil hole 2A provided in the rotation support part 2 corresponding to the hole 8G. A lubricating oil hole is provided. In the above operation, hydraulic oil is supplied to the C-2 hydraulic oil supply passage 3B by the operation of the hydraulic control device 400 when the clutch C2 is engaged, and the hydraulic oil is supplied to the hole 8F and the oil groove 8.
A and into the hydraulic servo C-2 through hole 1A. At this time, the hydraulic oil supplied to the C-2 hydraulic oil supply passage 3B is supplied to the gap A through the seal ring lubricating oil hole 6, and the hydraulic oil in the gap A is supplied to the front seal ring 5A.
Forcibly lubricate the front oil seal 5A. Since lubricating oil always flows through the lubricating oil supply path 3C during rotation of the input shaft 10, the gap B is connected to the lubricating hole 2A by the lubricating oil supply path 3C.

Lubricating oil is constantly supplied through the hole 8G, and the cylindrical rotating body 1
The outer circumferential member of the oil hole 1C provided in communication with the gap B and the outer circumference, the rear seal ring 5B, and the cylindrical bush 9 are lubricated. Further, as shown in Table 1 below, the power transmission to the cylindrical rotating body 1 of this embodiment is in the P (bulking) range, the N
In neutral) range, 2nd speed, power is not transmitted and the engine stops; in R (reverse) range, 3rd and 4th speeds, power is transmitted in the same direction as the intermediate transmission shaft, and only in 1st speed. Receives power transmission in the opposite direction to the intermediate transmission shaft 11. As a result, in the first speed, the cylindrical rotating body 1 is in the opposite direction to the intermediate transmission III 111, and the cylindrical bushing 9 also rotates in the opposite direction due to the sliding resistance of the cylindrical rotating body 1, so the inner circumference of the cylindrical bushing 9 Groove 9
Although not much lubricating oil can be supplied to the lubricated member arranged on the rear outer circumference of the cylindrical bushing 9 through A, the P range and N range
Range, 2nd speed is controlled by the oil pressure of the lubricating oil supplied to gap B, and the R range, which is frequently used when the vehicle is running,
During the third and fourth speeds, the cylindrical bushing 9 is also rotated in the same direction as the intermediate transmission shaft 11, so the lubricating oil supplied to the gap B is transferred to the cylinder through the inner periphery 9A of the cylindrical bushing 9. It lubricates lubricated members such as the bush 113C disposed on the rear outer periphery of the shaped bush 9.

A brake plate b2 of the brake B2 at the front and a brake plate b3 of the brake B3 at the rear are spline-fitted to a spline 136 formed on the inner periphery of the rear part of the transmission case 130. and an annular projection 31 on the front side.
A fourth hydraulic servo drum 32 is spline-fitted. An annular piston 33 for pressing the brake B2 is fitted between the outer circumferential wall 328 of the fourth hydraulic servo drum 32 and an annular protrusion 310, and a hydraulic servo B of the brake B2 is fitted between the annular screw 1-33 and the fourth hydraulic servo drum 32. −
2, and an annular piston 3 on the inner peripheral wall 32B side.
A return spring 34 is provided that presses the hydraulic servo B-3 toward the hydraulic servo B-2. Further, a one-way latch F1 with the sun gear shaft 29 as an inner race is provided on the inner circumference side of the brake B2, and the brake B2 is attached to the outer circumference of the outer race 35. A plurality of pistons 371 and 373 for pressing the brake B3 and a reaction sleeve 312 are fitted into an annular hole 36 formed between the outer circumferential side of the rear support 133 of the rear support wall 134 on the rear side of the brake B2 and the transmission case 130. Forms the hydraulic servo B-3 of the brake B3, and also the piston 371.373
Return spring 3 that presses the servo toward the hydraulic servo B-3 side
8 is supported by a return spring fitting 38A attached to the tip of the rear rib 1-133. The inner race 39 of the one-way latch F2 arranged on the inner periphery of the brake B3 is connected to the fourth hydraulic servo drum 32 on the outer periphery of the sun gear shaft 29, and the brake B3 is attached to the outer periphery of the outer race 40 of the one-way clutch F2. has been done. In the third planetary gear system (2), the ring gear S2 is connected to the sun gear shaft 29.
The 21st wheel rear P2 is connected to the outer race 40 of the front one-way latch F2, and is also connected to the brake B3. The circumferences are connected via a connecting member 42 that is spline-fitted. The parking gear 41 is provided so that a parking pawl 43 engages with the parking gear 41 to fix the output shaft 12 when the shift lever of the automatic transmission is selected to the parking (P) position.

The transmission 300 changes from 1 to transmission case 1 depending on vehicle driving conditions such as vehicle speed and throttle opening.
The engagement of each clutch and brake rake is controlled by hydraulic pressure selectively output to the hydraulic servo of each friction engagement device from a hydraulic control device 400 in a valve body 403 built in an oil pan 402 fastened to the lower part of the valve 30 by a bolt 401. The gears are engaged or released, resulting in four forward speeds or one reverse speed change. The operation of each clutch, brake, and one-way clutch and the gear position (RANGE) achieved
- Examples are shown in Table 1.

Table 1 In Table 1, E indicates that the corresponding clutch and brake are engaged, and × indicates that the corresponding clutch and brake are disengaged.

``Although the corresponding one-sided clutch is engaged in the engine drive state, this engagement is not necessarily required because the transmission of power is guaranteed by the clutch or brake built in parallel. Lock). (L) ゛ indicates that the corresponding one-sided clutch is engaged only in the engine drive state, and is not engaged in the engine brake state. Rana f indicates that the corresponding one-sided clutch is free Show that.

[Brief explanation of the drawing]

FIG. 1 is a sectional view, not showing the lubrication mechanism for the cylindrical rotational support of the present invention, FIG. 2 is a sectional view of an automatic transmission for a vehicle to which the lubrication mechanism for the cylindrical rotational support of the invention is applied, The figure is a front view of the support part support, and FIG. 4 is a perspective view of the cylindrical bushing.

Claims (1)

[Scope of Claims] 1) A cylindrical rotating body, and a seal ring and a cylindrical bush arranged on the inner periphery of the cylindrical rotating body and arranged between the cylindrical rotating body and the cylindrical rotating body. A cylindrical rotary body support mechanism comprising: a rotary support part that supports the cylindrical rotary body; a support part support having an oil passage through which lubricating oil flows; A gap is formed between the cylindrical bushes, a lubricating oil hole is provided in the gap through which the oil passage in the support portion flows, and a groove is provided in the cylindrical direction of the cylindrical bushing through which the lubricating oil flows. A lubrication mechanism for the cylindrical rotating support part.