JPS6141055A - Bypass circuit for lubricating oil - Google Patents

Abstract

PURPOSE:To promote the smooth discharge of lubricating oil discharged to the outer periphery of a fixed member by forming a peripheral groove and so on between a fixed member for dividing a speed change mechanism into one side speed change mechanism and the other side speed change mechanism, and a transmission case. CONSTITUTION:A transmission is provided with a fixed member 3 having a cylindrical support portion 3A projecting backward, which is disposed in the middle of its case 2. The fixed member 3 is adapted to divide into speed change mechanism chambers 1C and 1D where one side speed change mechanism 1A and the other side speed change mechanism 1B are respectively disposed. In this case, a peripheral groove 4B connected in the peripheral direction and a longitudinal groove 4A for connecting the peripheral groove 4B to the other side speed change mechanism chamber 10 are formed between the fixed member 3 and the transmission case 2. The peripheral groove 4B is provided with a longitudinal groove opening portion 4C formed at the side surface position of the longitudinal groove 4A, and a lower opening portion 4D for connecting the peripheral groove 4B to one side speed change mechanism chamber 1C below the longitudinal groove 4A.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a bypass circuit for quickly draining lubricating oil in an automatic transmission from between a transmission case and a fixed member.

[Prior Art] Conventionally, an automatic vehicle has a transmission case in which a transmission mechanism is disposed, and a fixing member disposed within the transmission case that partitions the transmission mechanism into one side transmission mechanism and the other side transmission mechanism. In a transmission, a rotating member is installed at the corner of a fixed member for the purpose of shortening the automatic transmission in the axial direction, and the lubricating oil released from the rotating member is transmitted to the surrounding members and drained downward. Ta.

[Problems to be Solved by the Invention] In the conventional technology described above, the lubricating oil released from the rotating member to the surrounding members is trapped between the rotating members, between the fixed member and the rotating member, etc. This causes oil to drag, causing deterioration in power transmission efficiency.In addition, when the transmission mechanism rotates at high speeds, such as when driving at high speeds, the lubricating oil foams due to agitation, and the oil temperature rises. There were concerns that this would cause negative effects such as deterioration of oil performance.

[Means for Solving the Problems] In order to solve the above problems, the lubricating oil bypass circuit of the present invention includes a transmission case 2 in which the transmission mechanism 1 is disposed, and a transmission case 2 disposed within the transmission case 2,
The transmission mechanism 1 is divided into one side transmission mechanism 1A and the other side transmission mechanism 1B.
In an automatic transmission having a fixing member 3 partitioning between the fixing member 3 and the transmission case 2, a circumferential groove 4B communicating in the circumferential direction is provided between the fixing member 3 and the transmission case 2; One or more longitudinal grooves communicating with at least one side of the mechanism 18 or the other side transmission mechanism 1B, and a position below the longitudinal grooves to drain the lubricating oil supplied in the circumferential groove 4B. The configuration is such that an opening 4D is provided.

[Function] The effects of the above configuration are as follows: - Among the lubricating oil released to the outer peripheral position of the fixed member 3 from the right side transmission mechanism 1A or the other side transmission mechanism 1B, the lubricating oil supplied to the vertical groove 48 is as follows. It flows out from an opening 4D provided at a position below the vertical groove 4A, such as a side or lower position, via a circumferential groove 4B opening into the vertical groove 4A.

[Effects of the Invention] The lubricating oil bypass circuit of the present invention having the above configuration includes a circumferential groove communicating in the circumferential direction between the fixed member and the transmission case, and a circumferential groove dIS connected to the right side gear shift am. or one or more vertical grooves that communicate with at least one side of the other side transmission mechanism, and an opening provided at a position below the vertical groove to drain the lubricating oil supplied into the circumferential groove.] By providing a section, the lubricating oil released on the outer periphery of the fixed member can be drained through the circumferential groove without leaking between the rotating members or between the fixed member and the rotating member. In addition to reducing the drag resistance caused by lubricating oil and improving power transmission efficiency, it also prevents agitation of lubricating oil by rotating members and eliminates negative effects such as oil temperature increase and oil foaming caused by agitation of lubricating oil. can.

[Example] First, a lubricating oil bypass circuit of the present invention will be explained based on an example shown in the drawings.

FIG. 1 is a sectional view showing a lubricating oil bypass circuit of the present invention, and FIG. 2 is a sectional view of an automatic transmission for a vehicle to which the lubricating oil bypass circuit of the present invention is applied.

Automatic transmission 1 100 is hydraulic torque converter 200
It consists of a transmission (41, etc.), a hydraulic control device &400, etc.

The transmission mechanism 1 includes a first planetary gear device UO1 oil f': [one side transmission mechanism 18 comprising one multi-disc clutch C01 operated by a servo, one multi-disc brake BO1 and one one-way latch FO; 2nd planetary gear system @U1, 3rd M heavy vehicle neck U2, two multi-disc clutches C1 and C2 operated by hydraulic servo, brake B to one bell 1
1. It is composed of the other side transmission mechanism 1B with three forward speeds and one reverse speed, which is equipped with two multi-disc brakes B2 and B3 and two one-way latches F1 and F2.

The transmission case 110 of the automatic transmission 100 includes a torque converter housing 120 that accommodates a torque converter 200, a transmission mechanism 1A on one side that is an overdrive transmission, and a transmission mechanism 1B on the other side that is an underdrive transmission. It consists of 1-transmission case 2, an extension housing 140 that surrounds the rear side of the automatic transmission 100, etc., which are integrally formed with respective chambers for accommodating , -F tension 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 runner 204 disposed opposite to the pump impeller 203, and a turbine shell 205 holding the turbine launch 204. , a stator 20 that is supported by a fixed shaft 207 connected to a transmission-like case 110 via a one-way clutch 206, and increases torque capacity when the input rotation speed is low.
8. The front cover 201 and the turbine shell 20
5) between the front cover 201 and the turbine seat 2
05 is provided with a direct coupling clutch (lock-up clutch) 209 that rotates 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 2 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 of the transmission case 2,
Extension member 21 connected to the inner peripheral end of rear cover 202
0 is spline-fitted to the inner circumference of the external gear 150a via the inner circumference of the cylindrical portion 151. Further, on the rear side of the oil pump body 152, an oil pump cover 154 is fastened to the right of a cylindrical front support 153 that is coaxial with the cylindrical part 151 and protrudes rearward, so that the oil pump housing 152 and the oil Pump cover 154 forms a partition between torque converter housing 120 and transmission case 2 . Further, in the middle of the transmission case 2, there is a rear wall that partitions one side transmission mechanism 18 1C in which one side transmission mechanism 18 is formed and the other side transmission mechanism chamber 1D in which a speed change mechanism 1B is formed. A fixing member 3 which is an intermediate support wall having a protruding cylindrical support portion 3A is provided.

The fixing member 3 has a circumferential groove 4B that communicates in the circumferential direction on the outer periphery, and a circumferential groove 48 and the other side transformer 1M1B on the upper outer periphery.
A vertical groove 4A communicating with the other side transmission mechanism chamber 1D is formed, and a circumferential groove 4B has a vertical opening 4 at a side position toward the vertical groove 4.
A lower opening 4° is formed at the lower position through which the circumferential groove 4B communicates with the one side transmission mechanism chamber 1C, and the lubricating oil released from the used side transmission mechanism 1B into the vertical groove 48 is ,
It flows into the circumferential groove 4B through the vertical groove opening 4C of the circumferential groove 4B that opens into the vertical groove, and flows into the lower opening 40 through the circumferential groove 4B.
More will be leaked. Rear of transmission case 2 (
On the right side of the figure, there is a cylindrical rear support 1 that protrudes forward.
A rear support wall 134 having 33 is provided.

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 mechanism 1, which is the output shaft of the torque converter 200, is rotatably supported inside the fixed shaft 207. The input shaft 10
has a flange portion 101 at the rear end, and a rearward hole 102 is formed in the center of the rear end. The input shaft 10
An intermediate power transmission shaft 11 arranged in series with the input shaft 10 is rotatably mounted at the rear of the input shaft 10, and the tip of the intermediate power transmission shaft 11 slides into the hole 102 of the input shaft 10. 1
1 has a flange portion 111 at its rear end, and a rearward-facing hole 112 is formed in the center of which the tip of an output shaft 12 that transmits power to the driving wheels slides. Output @ 12 has a rotation speed detection sensor rotor 121 and a speedometer drive gear 122 fixed in the extension housing 140, and the rear end has a spline groove on the outer periphery to fit a sleeve yoke that transmits power to the drive wheels. 123 is formed,
Extension housing 1 via sleeve yoke
40, and the front end is rotatably supported within the hole 112 in the middle @11.

The one-side transmission mechanism 18 is provided with a first planetary gear device UO behind the input shaft 10, whose ring gear RO is connected to the intermediate transmission shaft 11 via a seven-flange plate 113, and a planetary carrier PO is connected to the input shaft 10. The ring gear SO is connected to the flange portion 101 of the shaft 10, and is formed by the inner race shaft 13 of the one-way latch FO. A first hydraulic servo drum 14 that opens rearward is fixed to the inner race shaft 13 on the front side of the first M star gear unit UO, and an annular shape is formed between the outer circumferential wall 14A and the inner circumferential wall 14B of the first hydraulic servo drum 14. A clutch C into which the piston 15 is fitted engages and disengages the carrier PO and the first hydraulic servo drum 14
A return spring 16 forms the hydraulic servo C-0 of O and presses the annular piston 15 toward the hydraulic servo C-0 on the inner race shaft 13 side, and a clutch CO is installed inside the outer peripheral wall 14A. 1st through
Hydraulic servo drum 14 and inner race shaft 13 are connected to 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 a clutch CO and a brake BO are provided on the outer periphery between the outer race 17 and the transmission case 2. A piston 18 that presses the brake BO is fitted in front of the fixed member 3 at the rear of the BO, and a hydraulic servo B-o of the brake BO is formed between the piston 18 and the fixed member 3, and the inner periphery of the front end of the fixed member 3 A return spring 19 that presses the piston 18 toward the hydraulic servo B-0 is fitted into the portion 135.

In the other side transmission mechanism 1B, a second hydraulic servo drum 20 that opens rearward is rotatably fitted on the outer periphery of the support portion 3A of the fixed member 3, and the outer circumferential wall 20A and the inner circumferential wall 2 are connected to each other.
An annular piston 21 that presses the clutch C2 is fitted between the annular piston 21 and the second hydraulic servo drum 20, and a hydraulic pressure component C-2 of the clutch C2 is formed between the annular piston 21 and the second hydraulic servo drum 20. Return spring 22 that presses 21 toward the hydraulic servo C-2 side, outer peripheral wall 2
Clutch C2 is installed inside 0A. Said second
At the rear of the hydraulic servo drum 20, there is a third hydraulic servo drum 2 which is open to the rear and has an annular projection 23 at the front.
4 is fixed to the outer periphery of the flange portion 111 at the rear portion of the intermediate power transmission shaft 11, and a clutch C1 is connected between the rear end of the intermediate power transmission shaft 11, the outer peripheral wall 24A of the third hydraulic servo drum 24, and the outer periphery of the flange portion 111. The annular piston 25 is fitted to form the hydraulic servo C-1 of the clutch C1 between the annular screws 1 to 25 and the third hydraulic servo drum 24. A return spring 26 presses toward the servo C-1 side, and a clutch C2 is attached to the outer periphery of the annular protrusion 23, and the second and third hydraulic servo drums 20.2 are connected via the clutch C2.
4 are connected. A second planetary gear device U1 is provided behind the third hydraulic servo drum 24, and its ring gear R1 is provided in front of a rotation support member 27 that rotatably supports the ring gear R1 on the outer periphery of the output shaft 12. Installed protrudingly (
The third
The carrier P1 is connected to the hydraulic servo drum 24, is spline-fitted to the front outer periphery of the output shaft 12, and is connected to the ring gear S.
1 is integrally formed at the tip of a sun gear shaft 29 rotatably provided on the outer periphery of the output shaft 12.

In addition, the 2.3rd hydraulic servo drum 20.24 and the 2nd
A connecting drum 30 molded to cover the planetary gear unit U1 with a minimum space is fixed at its front end to the outer periphery of the second hydraulic servo drum 20, and its rear end is attached to the ring gear @ behind the second planetary gear unit U1. Belt brake B1 is connected to 29 and fixes and releases the connecting drum 30 on the outer peripheral side.
is provided.

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 2.
A fourth hydraulic servo drum 32, which is open to the front and has an annular projection 31 on the front side, is spline-fitted between the four hydraulic servo drums 3 and 3. An annular piston 33 for pressing the brake B2 is fitted between the outer peripheral wall 328 of the fourth hydraulic servo drum 32 and the annular protrusion 31, and a hydraulic servo B- of the brake B2 is fitted between the annular piston 33 and the fourth hydraulic servo drum 32. A return spring 34 is provided on the inner peripheral wall 32B side to press the annular piston 33 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. Rear support wall 134 on the rear side of brake B2
A plurality of pistons 371 and 313 for pressing the brake B3 and a reaction sleeve 372 are fitted into the annular hole 36 formed between the outer circumferential side of the rear support 133 and the transmission case 2, and the hydraulic servo B of the brake B3 is fitted.
A return spring 38 that forms the pistons 371 and 373 toward the hydraulic servo B-3 is supported by a return spring fitting 38A attached to the tip of the rear support 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 device U2, the Zang gear S2 is connected to the sun gear shaft 2.
9, the carrier P2 is connected to the outer race 40 of the front one-sided clutch F2, and is also connected to the brake B3, and a ring gear R2 having a parking gear 41 around the outer periphery is connected to the output shaft 12 with the inner periphery. They are connected via a spline-fitted connecting member 42. 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 mechanism 1 controls various friction coefficients from a hydraulic control device 400 in a valve body 403 built in an oil pan 402 fastened to the lower part of the transmission case 2 with bolts 401, depending on vehicle running conditions such as vehicle speed and throttle opening. By selectively outputting hydraulic pressure to the hydraulic servo of the coupling device,
Each clutch and brake is engaged or released;
It is designed to perform four forward gear shifts or one reverse gear shift.

Table 1 shows an example of the operation of each clutch, brake, and one-way clutch and the gear position (RANGE) achieved.

Table 1 In Table 1, E indicates that the corresponding clutch and brake are engaged, × indicates that the corresponding clutch and brake are disengaged, and 3L indicates that the corresponding one-way clutch is in engine drive state. However, this engagement is not necessarily required (locked) because power transmission is maintained by a clutch or brake installed in parallel. (L
) indicates that the corresponding one-way clutch is engaged only in the engine drive state and not in the engine brake state. Roughly f indicates that the corresponding one-way clutch is free.

FIG. 3 shows another embodiment of the invention.

In this embodiment, a circumferential groove 4B is formed on the inner circumferential side of the transmission case 2 at a position where the fixing member 3 is fitted therein, and a vertical groove 4A is formed on the one side transmission mechanism chamber 1C on the one side transmission mechanism 1A side and on the other side. The transmission mechanism chamber 1B side is provided in communication with the other transmission mechanism chamber 1D, and the circumferential groove 4B has a vertical groove opening 4C at the outer peripheral position of the vertical groove 4A formed on the fixed member 3 side. A lower opening 4D is provided at the upper position of the circumferential groove 4B by cutting the transmission case 2, and the lubricating oil released from the transmission mechanism 18 on one side and the transmission mechanism 1B on the other side is vertically The lubricating oil released into the groove flows into the circumference F+4B from the ffl groove opening 4C, passes through the circumferential groove 4B, and connects the transmission mechanism 18 on one side and the rotation member 1B on the other side. The liquid flows out from the lower opening 4D without coming into contact with the liquid.

[Brief explanation of drawings]

FIG. 1 is a sectional view showing a lubricating oil bypass circuit of the present invention;
FIG. 2 is a cross-sectional view of an automatic transmission for a vehicle to which the lubricating oil bypass circuit of the present invention is applied, and FIG. 3 is a cross-sectional view showing another embodiment of the present invention. In the figure 1... Speed change mechanism IA--ri speed measurement mechanism 1
B...Transmission mechanism on the other side 10...Transmission mechanism chamber on one side 1D...Transmission mechanism chamber on the other side 2...Transmission case 3...Fixed part IJ/IA...Vertical groove 4B... Circumferential groove 40... Full length opening 4D.
・・Downward opening 100・・Automatic transmission

Claims (1)

[Scope of Claims] 1) A transmission case in which a transmission mechanism is disposed, and a fixing member disposed within the transmission case that partitions the transmission mechanism into one side transmission mechanism and the other side transmission mechanism. In the automatic transmission, a circumferential groove communicating in a circumferential direction is provided between the fixed member and the transmission case, and the circumferential groove and at least one side of the one side transmission mechanism or the other side transmission mechanism are connected. A lubricating oil bypass comprising one or more communicating longitudinal grooves and an opening provided at a position below the longitudinal grooves to drain the lubricating oil supplied into the circumferential groove. circuit. 2) The lubricating oil bypass circuit according to claim 1, wherein the circumferential groove is formed on the outer periphery of the fixing member. 3) The lubricating oil bypass circuit according to claim 1, wherein the circumferential groove is formed on the inner periphery of the transmission case.