JP2014114877A - Automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress drive loss by drain oil from a cancellation chamber when providing the cancellation chamber for suppressing the fluctuation of fastening power of a piston part of a lock-up clutch according to the fluctuation of an internal pressure of a torque converter.SOLUTION: In an automatic transmission 1, in a torque converter 3, with a piston part 33c of a lock-up clutch 3f being sandwiched in-between, a hydraulic chamber 34b where fastening oil pressure is supplied and a cancellation chamber 34c communicated with a torque converter internal pressure chamber 34a via a throttle 39 are provided. A drain oil passage 65 for the cancellation chamber is provided for guiding a hydraulic oil in the cancellation chamber 34c to a transmission mechanism 5 side through a turbine shaft 4, and an oil drain port 66 of the drain oil passage is provided in a position which does not overlap with friction fastening elements 10 and 20 configuring the transmission mechanism 5, in an axial direction.

Description

  The present invention relates to an automatic transmission for a vehicle including a torque converter and a transmission mechanism, and belongs to the technical field of a transmission for a vehicle.

  Generally, an automatic transmission for an engine vehicle includes a transmission mechanism for shifting engine output and a torque converter for transmitting the engine output to the transmission mechanism.

  The torque converter includes a pump that rotates integrally with the crankshaft of the engine, a turbine that is disposed opposite to the pump and driven by fluid by the pump, and is disposed inside an opposed portion of the pump and the turbine. And a stator for increasing torque. Also, in order to improve the fuel efficiency of the engine, the lockup that directly connects the pump and the turbine is excluded except when starting using torque increasing action or when the gearbox needs to allow relative rotation of the pump and turbine. A clutch may be provided.

  In this type of torque converter, a hydraulic chamber is formed on one side of the lock-up clutch between which the piston portion (lock-up piston) is sandwiched. The lockup clutch is fastened by applying a fastening force to the plate. Further, the lock-up clutch can be slip-controlled by adjusting the fastening hydraulic pressure or the fastening force supplied to the hydraulic chamber. By performing this slip control, engine torque fluctuations can be effectively absorbed.

  By the way, the case of the torque converter is filled with hydraulic oil for transmitting power between the pump and the turbine. The hydraulic pressure (internal pressure) in the case is determined by the rotation speed of the pump and the rotation of the turbine. It fluctuates greatly with changes in speed and speed ratio of the pump and turbine. When such an internal pressure acts on the lockup piston from the side opposite to the hydraulic chamber, the fastening force acting on the friction plate with respect to a constant fastening hydraulic pressure fluctuates as the internal pressure fluctuates. It is difficult to precisely control the fastening control and slip control. Also, considering the fluctuation of the internal pressure that fluctuates the fastening force in this way, it is necessary to set the fastening hydraulic pressure higher in order to correspond to the state where the internal pressure becomes the highest, so a high-capacity hydraulic pump is required, and as a result As a result, an increase in engine load and a deterioration in fuel consumption are caused.

  In order to solve this problem, for example, as disclosed in FIG. 3 of Patent Document 1, a cancel chamber may be provided on the opposite side of the hydraulic chamber with the lockup piston interposed therebetween. The cancel chamber is provided so as to communicate with the internal pressure chamber via a throttle (orifice). As a result, a hydraulic pressure lower than the internal pressure is stably supplied to the cancel chamber via the throttle, and the internal pressure in the case can be prevented from acting on the lockup piston from the counter-hydraulic chamber side. Therefore, it is possible to suppress the change in the fastening force of the lockup clutch due to the change in the internal pressure, thereby making it possible to precisely perform the engagement control and slip control of the lockup clutch.

US Patent Application Publication No. 2010/0084238

  By the way, the above-mentioned Patent Document 1 does not describe how to discharge the hydraulic oil introduced into the cancellation chamber. Generally, however, the turbine shaft (the output shaft of the torque converter, that is, the speed change mechanism) is not described. It is conceivable to provide an oil discharge passage for guiding the oil discharged from the cancel chamber to the transmission mechanism side, and to use the oil discharged through the oil discharge passage as lubricating oil in the transmission mechanism.

  However, when the drainage oil guided by the drainage passage in the turbine shaft is introduced into the transmission mechanism as the lubricant, the supply of the lubricant to the frictional engagement elements such as the clutch and the brake in the transmission mechanism becomes excessive, There is a concern that the rotational resistance due to the viscosity received by the frictional engagement element during release increases. Then, an increase in driving loss and an increase in fuel consumption of the engine are caused.

  Therefore, the present invention provides a cancel chamber for suppressing the fastening force of the piston portion of the lock-up clutch from fluctuating with the fluctuation of the internal pressure in the torque converter. It is an object of the present invention to provide an automatic transmission that can suppress drive loss.

  In order to solve the above problems, the present invention is configured as follows.

First, the invention according to claim 1 of the present application is
A torque converter;
A transmission mechanism in which the output of the torque converter is input via a turbine shaft;
The torque converter includes a lock-up clutch that connects an input side and an output side thereof,
An automatic transmission provided in the torque converter with a hydraulic chamber to which a fastening hydraulic pressure is supplied across a piston portion of the lockup clutch and a cancel chamber communicated with the torque converter internal pressure chamber via a throttle. There,
An oil discharge passage for the cancel chamber is provided that guides the hydraulic oil in the cancel chamber to the transmission mechanism side through the turbine shaft.
The oil discharge port of the oil discharge passage for the cancel chamber is provided in a position in the axial direction so as not to overlap with a frictional engagement element constituting the speed change mechanism.

According to a second aspect of the present invention, in the automatic transmission according to the first aspect,
The transmission mechanism includes a frictional engagement element including a centrifugal balance chamber that axially overlaps the turbine shaft,
An oil discharge passage for the centrifugal balance chamber that discharges hydraulic oil from the centrifugal balance chamber is formed so as to join the oil discharge passage for the cancel chamber and communicate with the oil discharge port.

Furthermore, the invention according to claim 3 is the automatic transmission according to claim 2,
In the transmission case, a partition wall that partitions the accommodating portion of the torque converter and the accommodating portion of the transmission mechanism is provided,
A boss portion through which the turbine shaft passes is provided in the partition wall so as to extend in the axial direction toward the speed change mechanism,
One oil hole formed in the peripheral wall of the boss portion constitutes an oil passage from the junction of the oil discharge passage for the cancellation chamber and the oil discharge passage for the centrifugal balance chamber toward the oil discharge port. It is characterized by.

Furthermore, the invention according to claim 4 is the automatic transmission according to claim 3, wherein
In the turbine shaft, a first oil passage that constitutes an oil discharge passage for the cancellation chamber, and a second oil passage that constitutes an oil supply passage that supplies fastening hydraulic pressure to the hydraulic chamber are provided,
In the peripheral wall of the boss portion, a third oil passage that constitutes a downstream portion of the oil discharge passage for the cancel chamber from the first oil passage, and an upstream portion of the second oil passage in the oil supply passage. A fourth oil passage is provided,
On the outer peripheral surface of the turbine shaft, an outlet of the first oil passage and an inlet of the second oil passage are provided,
On the inner peripheral surface of the boss portion, an inlet of the third oil passage and an outlet of the fourth oil passage are provided,
In the fitting portion between the outer peripheral surface of the turbine shaft and the inner peripheral surface of the boss portion, an axial torque is interposed across an oil discharge communicating portion that communicates the outlet of the first oil passage and the inlet of the third oil passage. A first seal member that partitions the converter side from the internal pressure chamber communicating portion that communicates with the internal pressure chamber of the torque converter includes an outlet of the fourth oil passage and an inlet of the second oil passage on the axial anti-torque converter side. The second seal members for partitioning between the communicating portions for refueling to be communicated are respectively mounted in seal ring grooves provided on the outer peripheral surface of the turbine shaft.

  With the above configuration, according to the invention of each claim of the present application, the following effects can be obtained.

  First, according to the automatic transmission according to the invention described in claim 1 of the present application, the cancel for suppressing the fastening force of the piston portion of the lock-up clutch from fluctuating with the fluctuation of the internal pressure in the torque converter. When the chamber is provided, the oil discharge port of the oil discharge passage for the cancel chamber is provided at a position that does not overlap with the frictional engagement element constituting the transmission mechanism in the axial direction of the turbine shaft. The discharged oil can be prevented from adhering to the frictional engagement element. For this reason, an increase in rotational resistance due to the viscosity that the frictional engagement element receives at the time of release is suppressed, and thus it is possible to suppress drive loss.

  According to the second aspect of the present invention, the oil discharge passage for the centrifugal balance chamber that discharges the hydraulic oil from the centrifugal balance chamber of the frictional engagement element that constitutes the speed change mechanism is the oil discharge passage for the cancel chamber. Since they merge and communicate with the oil discharge port, the hydraulic oil in the centrifugal balance chamber can be discharged so as not to adhere to the frictional engagement element by using the oil discharge passage for the cancel chamber. Further, compared to the case where the oil discharge passage for the centrifugal balance chamber is formed completely independently from the oil discharge passage for the cancel chamber, the manufacture of the automatic transmission can be simplified and reduced in size.

  Furthermore, when the invention according to claim 3 is applied to the invention according to claim 2, one oil hole formed in the peripheral wall of the boss portion in the partition wall in the transmission case is provided with a discharge for the cancel chamber. Since an oil passage from the junction of the oil passage and the oil discharge passage for the centrifugal balance chamber to the oil discharge port is configured, two oil holes are formed in the peripheral wall of the boss portion for the two oil discharge passages. Compared with the case of forming the boss portion, the boss portion can be reduced in size and strength.

  Furthermore, when the invention according to claim 4 is applied to the invention according to claim 3, an oil drain passage for the cancel chamber is provided at the fitting portion between the outer peripheral surface of the turbine shaft and the inner peripheral surface of the boss portion. The first oil passage in the turbine shaft and the third oil passage in the peripheral wall of the boss are respectively connected to the oil discharge communicating portion and the internal pressure chamber communicating portion communicating with the torque converter internal pressure chamber. An oil supply communication portion that communicates a second oil passage in the turbine shaft and a fourth oil passage in the peripheral wall of the boss portion, each of which is partitioned and that constitutes an oil supply passage that supplies the fastening oil pressure of the lockup clutch, and the oil discharge The communication portion is partitioned by the second seal member. According to this configuration, an internal pressure higher than the exhaust pressure from the cancel chamber is always applied to the internal pressure chamber communication portion, and the oil supply communication portion is disconnected from the cancel chamber during lockup clutch engagement and slip control. A hydraulic pressure higher than the exhaust pressure acts. For this reason, during the lockup clutch engagement and slip control, the first seal member and the second seal member are maintained in the state of being moved toward the oil discharge communicating portion in the seal ring groove due to the above pressure difference. As a result, good sealing properties can be obtained. In particular, since the sealing performance of the second seal member is improved, the fastening hydraulic pressure of the lockup clutch can be controlled with high accuracy, and slip control requiring particularly precise control can be performed satisfactorily.

1 is a skeleton diagram of an automatic transmission according to an embodiment of the present invention. It is a table | surface which shows the relationship between the combination of fastening of a friction element, and a gear stage. It is sectional drawing which shows a part of structure of the automatic transmission which concerns on 1st Embodiment. FIG. 4 is an enlarged sectional view showing a seal structure of a gap between an outer peripheral surface of a turbine shaft and an inner peripheral surface of a boss portion in the automatic transmission shown in FIG. 3. It is sectional drawing which shows a part of structure of the automatic transmission which concerns on 2nd Embodiment.

  Hereinafter, embodiments of the present invention will be described.

  FIG. 1 is a skeleton diagram showing a configuration of an automatic transmission 1 according to the present embodiment. The automatic transmission 1 is applied to an engine horizontal type vehicle such as a front engine front drive vehicle.

  As shown in FIG. 1, an automatic transmission 1 includes, as main components, a torque converter 3 attached to an engine output shaft 2 and a speed change mechanism in which output rotation of the torque converter 3 is input via a turbine shaft 4. And 5. The turbine shaft 4 functions as an output shaft of the torque converter 3 and an input shaft of the speed change mechanism 5.

Hereinafter, for convenience of explanation, the engine side (right side in the figure) will be described as the front side and the non-engine side (left side in the figure) as the rear side with respect to the axial direction of the turbine shaft 4.

  The torque converter 3 includes a case 3a connected to the engine output shaft 2, a pump 3b fixed in the case 3a, and disposed opposite to the pump 3b and driven by the pump 3b via hydraulic oil. A turbine 3c and a stator 3e interposed between the pump 3b and the turbine 3c and supported by the transmission case 6 via a one-way clutch 3d to generate a torque increasing action are provided. The rotation of the turbine 3 c is transmitted to the transmission mechanism 5 through the turbine shaft 4 as the output rotation of the torque converter 3.

  The torque converter 3 includes a lock-up clutch 3f that couples the case 3a on the input side and the turbine 3c on the output side. By connecting the case 3a and the turbine 3c by the lock-up clutch 3f, the engine output shaft 2 is directly connected to the turbine 3c through the case 3a.

  The transmission mechanism 5 is accommodated in the transmission case 6 in a state of being disposed on the axis of the turbine shaft 4. The transmission case 6 includes a main body 6a that forms an outer periphery, a pump storage wall 6b that stores a mechanical oil pump 30 that is driven by the engine via the torque converter 3, and a rear side of the main body 6a. And an end cover 6c that closes the open end of the. The transmission case 6 is configured to accommodate the torque converter 3 together with the transmission mechanism 5, and the pump storage wall portion 6 b is provided in the transmission case 6 with the accommodating portion of the torque converter 3 and the transmission mechanism 5. It functions as a partition wall that partitions the housing portion.

  The speed change mechanism 5 includes a first clutch 10 and a second clutch 20 to which power from the torque converter 3 is input via the turbine shaft 4 and a first power to which power from one or both of these clutches 10 and 20 is input. 1, 2nd and 3rd planetary gear sets (hereinafter simply referred to as “first, second and third gear sets”).

  The first clutch 10 and the second clutch 20 are disposed so as to overlap in the axial direction, and the first clutch 10 is disposed on the radially outer side of the second clutch 20. A first gear set 40, a second gear set 50, and a third gear set 60 are arranged in order from the front side on the rear side of the first and second clutches 10 and 20. In the axial direction, an output gear 7 is disposed between the first and second clutches 10 and 20 and the first gear set 40. The output gear 7 transmits the output rotation of the speed change mechanism 5 to the differential device 9 via the counter drive mechanism 8, whereby the left and right axles 9a and 9b are driven.

  The transmission mechanism 5 includes a first brake 70, a second brake 80, and a third brake 90 as friction elements other than the first and second clutches 10 and 20, and these brakes 70, 80, 90 are Arranged in this order from the front side. Furthermore, the speed change mechanism 5 includes a one-way clutch 100 disposed in parallel with the first brake 70.

  The first, second, and third gear sets 40, 50, and 60 are all single-pinion type planetary gear sets, and are respectively sun gears 41, 51, and 61, and a plurality of pinions that mesh with the sun gears 41, 51, and 61, respectively. 42, 52, 62, carriers 43, 53, 63 that support these pinions 42, 52, 62, and ring gears 44, 54, 64 that mesh with the plurality of pinions 42, 52, 62.

  The turbine shaft 4 is directly connected to the sun gear 61 of the third gear set 60. The sun gear 41 of the first gear set 40 and the sun gear 51 of the second gear set 50 are connected to each other, the ring gear 44 of the first gear set 40 and the carrier 53 of the second gear set 50 are connected to each other, and the ring gear of the second gear set 50 is connected. 54 and the carrier 63 of the third gear set 60 are connected to each other. Further, the output gear 7 is connected to the carrier 43 of the first gear set 40.

  Further, the sun gear 41 of the first gear set 40 and the sun gear 51 of the second gear set 50 are connected to the output member 11 of the first clutch 10, whereby the turbine shaft 4 can be connected and disconnected via the first clutch 10. It is connected to. Further, the carrier 53 of the second gear set 50 is coupled to the output member 21 of the second clutch 20, and is thereby coupled to the turbine shaft 4 so as to be connectable / disengageable via the second clutch 20.

  With the above configuration, according to the automatic transmission 1, the sixth forward speed and the reverse speed are achieved by combining the engagement states of the first and second clutches 10 and 20 and the first, second, and third brakes 70, 80, and 90. The relationship between the combination of the engagement states and the gear positions is as shown in the engagement table of FIG.

  As shown in FIG. 2, the first clutch 10 is a low clutch that is engaged at a relatively low speed (first to fourth speed), and the second clutch 20 is a relatively high speed (fourth to fourth). The high clutch is engaged at the sixth speed). 2, the first brake 70 is engaged in the engine brake operating range, and the one-way clutch 100 is locked in place of the first brake 70 in the D range or the like. Thus, the first speed is realized, but the first brake 70 may be engaged at the first speed such as the D range.

  Hereinafter, a characteristic configuration of the automatic transmission 1 will be described for each embodiment.

[First Embodiment]
The configuration of the characteristic part of the automatic transmission 1 according to the first embodiment will be described with reference to FIGS. 3 and 4.

  First, the configuration of the front side portion of the automatic transmission 1 will be described with reference to FIG. In FIG. 3, some or all of the constituent members of the torque converter 3 are not shown.

  As shown in FIG. 3, an oil hole 35 is formed in the turbine shaft 4 so as to extend from the front end surface to the axial rear side. A pipe member 36 is fitted into the oil hole 35, and the inside of the oil hole 35 is partitioned into an oil passage 65 a outside the pipe member 36 and an oil passage 55 a inside the pipe member 36. The pipe member 36 is shorter than the oil hole 35, and a gap 55 e is formed in the oil hole 35 on the rear side of the rear side end portion of the pipe member 36.

  The inner peripheral portion of the turbine 3c of the torque converter 3 is constituted by a boss-like turbine hub 33f. The turbine hub 33f is externally fitted to the front side end portion of the turbine shaft 4, and the rear side portion of the turbine hub 33f is spline fitted to the turbine shaft 4. As a result, the driving force of the turbine 3 c is transmitted to the transmission mechanism 5 via the turbine shaft 4.

  The case 3a of the torque converter 3 has a front half formed of a front cover 33a connected to the engine output shaft 2, and a rear half formed of a pump shell 33b that forms an outer shell of the pump 3b. Yes. A boss portion 33e extending toward the rear side in the axial direction is provided on the inner peripheral portion of the front cover 33a, and the front side end portions of the turbine shaft 4 and the turbine hub 33f are fitted inside the boss portion 33e. In the internal space of the boss portion 33e, a gap 55d is formed on the front side of the front end surfaces of the turbine shaft 4 and the turbine hub 33f. On the other hand, a sleeve 33g extending toward the rear side in the axial direction is provided at the inner peripheral end of the pump shell 33b.

  Between the front cover 33a and the turbine 3c, a lock-up piston 33c as a piston portion of the lock-up clutch 3f and a seal plate 33d are arranged in this order from the front side. The lock-up piston 33c and the seal plate 33d are attached to the outer peripheral portion of the boss portion 33e.

  The case 3 a of the torque converter 3 is filled with hydraulic oil supplied from the oil pump 30. In this specification, the oil pressure in the case 3a is defined as “internal pressure”, and the space in which the internal pressure is generated in the case 3a is defined as “torque converter internal pressure chamber” (hereinafter simply referred to as “internal pressure chamber 34a”). To do.

  In the torque converter 3, the space on the rear side across the seal plate 33d constitutes a part of the internal pressure chamber 34a, and the engagement hydraulic pressure of the lockup clutch 3f is between the lockup piston 33c and the seal plate 33d. Is formed.

  When hydraulic pressure is introduced into the hydraulic chamber 34b from an oil supply passage 55 described later, the lockup piston 33c operates in the fastening direction (direction toward the front side in the axial direction). A friction plate (not shown) connected to the turbine 3c is pressed against the front cover 33a from the rear side by the lockup piston 33c, whereby the lockup clutch 3f is fastened.

  In the engagement control of the lock-up clutch 3f, in order to suppress a shock at the time of engagement of the clutch 3f, the engagement hydraulic pressure supplied to the hydraulic chamber 34b is controlled so that the clutch 3f is once slipped, and then completely To conclude.

  In the torque converter 3, a cancel chamber 34c is formed on the opposite side of the hydraulic chamber 34b with the lock-up piston 33c interposed therebetween, that is, between the front cover 33a and the lock-up piston 33c. The cancel chamber 34c is communicated with the internal pressure chamber 34a through a throttle 39 formed of an oil hole penetrating the boss portion 33e, for example.

  As a result, a hydraulic pressure lower than the internal pressure is stably supplied to the cancel chamber 34c through the throttle 39, and the internal pressure in the case 3a is prevented from acting on the lockup piston 33c from the counter-hydraulic chamber side. it can. Therefore, it is possible to suppress fluctuations in the fastening force of the lockup clutch 3f due to fluctuations in the internal pressure, thereby making it possible to precisely perform fastening control and slip control of the lockup clutch 3f. The hydraulic oil in the cancel chamber 34c is discharged to the transmission mechanism 5 side through an oil discharge passage 65 described later.

  The oil pump 30 includes a pair of inner and outer pump gears 31, and the pump gear 31 is interposed between a pump housing wall 6 b of the transmission case 6 and a pump cover 32 disposed on the front side of the pump housing wall 6 b. It is stored. The inner pump gear 31 is engaged with the rear side end portion of the sleeve 33g, whereby the oil pump 30 is driven by the rotation of the engine output shaft 2 via the case 3a and the sleeve 33g. .

  A pump sleeve 6e extending toward the axial front side (torque converter side) and a boss portion 6d extending toward the axial rear side (transmission mechanism side) are provided at the inner peripheral end of the pump storage wall 6b.

  The pump sleeve 6e is interposed between the outer peripheral surface of the turbine shaft 4 and the inner peripheral surface of the sleeve 33g. An oil supply passage 59 for supplying hydraulic oil to the internal pressure chamber 34a of the torque converter 3 is formed between the outer peripheral surface of the pump sleeve 6e and the inner peripheral surface of the sleeve 33g, and the inner peripheral surface of the pump sleeve 6e and the turbine shaft 4 An oil drainage passage 69 for discharging hydraulic oil from the internal pressure chamber 34a is formed between the outer peripheral surface and the outer peripheral surface. A one-way clutch 3d of the torque converter 3 is spline-fitted to the outer peripheral portion of the front end portion of the pump sleeve 6e.

  The turbine shaft 4 is penetrated inside the boss portion 6d, and a low clutch (first clutch) 10 and a high clutch (second clutch) 20 are disposed outside the boss portion 6d. A plurality of oil holes including oil holes constituting oil passages 55b and 65b, which will be described later, are provided in the peripheral wall of the boss portion 6d at intervals in the circumferential direction.

  The low clutch 10 includes a drum 12 and a hub 13 disposed inside thereof. An inner peripheral end portion of the drum 12 is coupled to a boss-like base portion 38 disposed on the outer peripheral portion of the boss portion 6d. The base portion 38 is provided so as to protrude from the boss portion 6 d toward the axial rear side, and the rear side protruding portion 38 a of the base portion 38 is spline-fitted to the outer peripheral portion of the turbine shaft 4. On the other hand, the inner peripheral end of the hub 13 is coupled to the sleeve-shaped output member 11 through which the turbine shaft 4 passes.

  Between the drum 12 and the hub 13, a plurality of friction plates 14 that are alternately engaged with these are disposed. A hydraulic chamber 18 to which fastening hydraulic pressure is supplied is formed between the piston 15 and the drum 12 for fastening the friction plates 14. A seal plate 16 is disposed on the opposite side of the hydraulic chamber 18 across the piston 15, and a return spring 17 that urges the piston 15 in the anti-fastening direction is interposed between the piston 15 and the seal plate 16. Yes.

  A centrifugal balance chamber 19 is formed between the piston 15 and the seal plate 16 on the opposite side of the hydraulic chamber 18 across the piston 15. By supplying the hydraulic oil to the centrifugal balance chamber 19, drag resistance caused by the residual hydraulic oil in the hydraulic chamber 18 when the low clutch 10 is released is suppressed, and the release control of the low clutch 10 can be performed with high accuracy. it can. Further, since the engagement and slip control of the low clutch 10 are performed on the assumption that the hydraulic oil is supplied to the centrifugal balance chamber 19, the low clutch can be obtained by appropriately supplying the hydraulic oil to the centrifugal balance chamber 19. 10 can be precisely controlled.

  The configuration of the high clutch 20 is substantially the same as that of the low clutch 10. That is, the high clutch 20 includes a drum 22 and a hub 23 disposed inside thereof. The inner peripheral end portion of the drum 22 is coupled to the base portion 38, similarly to the drum 12 of the low clutch 10. An inner peripheral end of the hub 23 is coupled to the output member 21 interposed between the outer peripheral surface of the turbine shaft 4 and the inner peripheral surface of the output member 11.

  Between the drum 22 and the hub 23, a plurality of friction plates 24 that are alternately engaged with these are disposed. A hydraulic chamber 28 to which fastening hydraulic pressure is supplied is formed between the piston 25 and the drum 22 for fastening the friction plates 24. A seal plate 26 is disposed on the opposite side of the hydraulic chamber 28 across the piston 25, and a return spring 27 that urges the piston 25 in the anti-fastening direction is interposed between the piston 25 and the seal plate 26. Yes.

  A centrifugal balance chamber 29 is formed between the piston 25 and the seal plate 26 on the opposite side of the hydraulic chamber 28 across the piston 25. By appropriately supplying hydraulic oil to the centrifugal balance chamber 19, release control of the high clutch 20, engagement control, and slip control can be performed precisely.

  Hereinafter, the configuration of the oil supply passage 55 that supplies the fastening hydraulic pressure to the hydraulic chamber 34b of the torque converter 3 and the oil discharge passage 65 that discharges the hydraulic oil from the cancel chamber 34c of the torque converter 3 will be described.

  As shown in FIG. 3, the oil supply passage 55 is provided so as to guide the fastening hydraulic pressure supplied from the oil pump 30 to the hydraulic chamber 34 b through the oil passage 55 a inside the pipe member 36 in the turbine shaft 4.

  Specifically, the oil supply passage 55 includes, in order from the upstream side, an oil passage 55b provided in the peripheral wall of the boss portion 6d, and the boss extending from the oil passage 55b toward the inner peripheral side of the boss portion 6d. An oil passage 55g provided in the portion 6d, an oil passage 55f extending from the oil hole 35 in the turbine shaft 4 toward the outer peripheral side so as to communicate with the oil passage 55g, and the oil passage 55f. Thus, the gap 55e disposed in the oil hole 35, the oil passage 55a inside the pipe member 36 disposed so as to communicate with the clearance 55e, and the front cover so as to communicate with the oil passage 55a. The gap 55d disposed in the internal space of the boss portion 33e of 33a, and an oil passage 55c formed on the peripheral wall of the boss portion 33e so as to communicate the gap 55d and the hydraulic chamber 34b of the torque converter 3 are provided. .

  The oil passage 55b extends from the rear side end face of the peripheral wall of the boss portion 6d toward the pump storage wall portion 6b toward the front side in the axial direction, and communicates with the discharge portion of the oil pump 30 in the pump storage wall portion 6b. Is provided. The rear end of the oil passage 55b is closed by a plug 37. A plurality of the oil passages 55f in the peripheral wall of the turbine shaft 4 are provided at intervals in the circumferential direction.

  When the fastening hydraulic pressure is supplied from the oil pump 55 to the hydraulic chamber 34b through the oil supply passage 55 configured in this way, the lockup piston 33c operates in the fastening direction as described above.

  On the other hand, the oil discharge passage 65 is provided so as to guide the hydraulic oil in the cancel chamber 34 c to the transmission mechanism 5 side through the oil passage 65 a outside the pipe member 36 in the turbine shaft 4.

  Specifically, the oil drainage passage 65 is provided in the boss portion 33e so as to extend from the portion constituting the cancel chamber 34c on the outer peripheral surface of the boss portion 33e of the front cover 33a toward the inner peripheral side in order from the upstream side. An oil passage 65c, an oil passage 65d provided in a radial direction through the peripheral wall of the turbine hub 33f so as to be able to communicate with the oil passage 65c, and a peripheral wall of the turbine shaft 4 so as to communicate with the oil passage 65d. And an oil passage 65a formed on the outside of the pipe member 36 in the oil hole 35 of the turbine shaft 4 so as to communicate with the oil passage 65e, and the oil passage 65e. An oil passage 65f provided through the peripheral wall of the turbine shaft 4 so as to communicate with the downstream portion of 65a, and a radially outer side from the inner peripheral surface of the peripheral wall of the boss portion 6d so as to communicate with the oil passage 65f. An oil passage 65g, which is provided to extend, and an oil passage 65b provided in the peripheral wall of the boss portion 6d so as to communicate with the oil passage 65g.

  A plurality of sets of the oil passages 65d and 65e communicating with each other are provided on the peripheral walls of the turbine hub 33f and the turbine shaft 4 at intervals in the circumferential direction. A plurality of the oil passages 65f in the peripheral wall of the turbine shaft 4 are also provided at intervals in the circumferential direction.

  The oil passage 65b extends from the rear side end face of the peripheral wall of the boss portion 6d toward the pump storage wall portion 6b toward the front side in the axial direction, and then bends radially outward at the pump storage wall portion 6b. The wall 6b extends to the surface on the transmission mechanism 5 side.

  The oil discharge port 66 of the oil discharge passage 65 is configured by an outlet of the oil passage 65b on the surface of the pump housing wall 6b on the transmission mechanism 5 side. In addition, since the centrifugal force does not act on the pump housing wall portion 6b and the boss portion 6d provided with the oil passage 65b, the oil discharge port 66 formed from the outlet of the oil passage 65b is connected to the oil discharge port 66. In order to realize smooth oil drainage, it is preferable to be disposed below the axis of the turbine shaft 4.

  The oil discharge port 66 is disposed offset to the front side in the axial direction with respect to the low clutch 10 and the high clutch 20, and the oil discharged from the oil discharge port 66 is connected to the drum 12 of the low clutch 10, It is guided between the pump housing wall 6b.

  Therefore, it is possible to prevent the oil discharged from the oil discharge port 66 from adhering to the friction plates 14 and 24 of the low clutch 10 and the high clutch 20. Therefore, an increase in rotational resistance due to the viscosity received by the friction plates 14 and 24 when the clutches 10 and 20 are released is suppressed, and thereby the driving loss of the turbine shaft 4 can be suppressed.

  Further, since the low clutch 10 and the high clutch 20 are the frictional engagement elements disposed on the most front side in the transmission mechanism 5, the oil discharge port 66 is configured so that all the components constituting the transmission mechanism 5 are arranged in the axial direction. It is provided at a position where it does not overlap with the frictional engagement element. Therefore, it is possible to reliably suppress an increase in the rotational resistance of the frictional engagement element of the transmission mechanism 5 due to the oil discharged from the oil discharge port 66.

  Incidentally, an oil passage 67a penetrating in the radial direction is formed in the rear side protruding portion 38a of the base portion 38 fitted on the boss portion 6d. A plurality of the oil passages 67a are provided at intervals in the circumferential direction. As a result, the hydraulic oil in the centrifugal balance chamber 29 of the high clutch 20 is discharged to the inner peripheral side of the rear side protruding portion 38a through the oil passage 67a. That is, the oil passage 67 a constitutes a drainage passage 67 for the centrifugal balance chamber that discharges the hydraulic oil from the centrifugal balance chamber 29.

  The outlet of the oil passage 67a constituting the oil discharge passage 67 for the centrifugal balance chamber is disposed adjacent to the rear side of the rear side end face of the peripheral wall of the boss portion 6d. Further, the rear side end of the oil passage 65b constituting the oil discharge passage 65 for the cancel chamber 34c is opened in the boss portion 6d. Therefore, the oil discharged from the centrifugal balance chamber 29 discharged from the oil passage 67a is introduced into the oil passage 65b of the boss portion 6d from the rear side open end. On the other hand, the oil discharged from the cancel chamber 34c introduced into the oil passage 65b is pushed into the front side by the oil discharged from the centrifugal balance chamber 29 introduced from the rear open end of the oil passage 65b. The oil is guided to the oil discharge port 66 together with the oil discharged from the centrifugal balance chamber 29. In this way, the oil discharge passage 67 for the centrifugal balance chamber is formed so as to join the oil discharge passage 65 for the cancel chamber and communicate with the oil discharge port 66.

  Therefore, the hydraulic oil in the centrifugal balance chamber 29 can be discharged so as not to adhere to the friction plate 24 by using the oil discharge passage 65 for the cancel chamber. Further, compared to the case where the oil discharge passage 67 for the centrifugal balance chamber is formed completely independently from the oil discharge passage 65 for the cancellation chamber, the manufacture of the automatic transmission 1 can be simplified and reduced in size. . In particular, the oil passage 65b from the junction of the oil discharge passage 65 for the cancellation chamber and the oil discharge passage 67 for the centrifugal balance chamber to the oil discharge port 66 is one oil hole formed in the peripheral wall of the boss portion 6d. Therefore, compared with the case where two oil holes are formed in the peripheral wall of the boss portion 6d for the two oil drain passages 65 and 67, the boss portion 6d can be reduced in size and strength. Can do.

  Next, the configuration of the fitting portion between the outer peripheral surface of the turbine shaft 4 and the inner peripheral surface of the boss portion 6d will be described with reference to FIG.

  As shown in FIG. 4, on the outer peripheral surface of the turbine shaft 4, an outlet of the oil passage (first oil passage described in claims) 65 f constituting the drain oil passage 65 for the cancel chamber 34 c, and hydraulic pressure An inlet of the oil passage (second oil passage described in claims) 55f constituting the oil supply passage 55 for the chamber 34b is provided. The oil passage 55f is disposed on the rear side of the oil passage 65f.

  On the other hand, on the inner peripheral surface of the boss portion 6d, an inlet of the oil passage (third oil passage described in claims) 65g constituting the downstream portion of the oil passage 65 from the oil passage 65f, An outlet of the oil passage (the fourth oil passage described in the claims) 55g (see FIG. 3) constituting the upstream portion of the oil passage 55 from the oil passage 55f is provided. The oil passage 55g is disposed on the rear side of the oil passage 65g (see FIG. 3).

  The outlet of the oil passage 65f constituting the oil discharge passage 65 and the inlet of the oil passage 65g are disposed so as to overlap in the axial direction, and the outer peripheral surface of the turbine shaft 4 at an axial position including this overlap portion. In the fitting portion between the boss portion 6d and the inner peripheral surface of the boss portion 6d, an oil draining communication portion 91a that continuously connects the outlet of the oil passage 65f and the inlet of the oil passage 65g is formed in the circumferential direction.

  On the other hand, the outlet of the oil passage 55g (see FIG. 3) constituting the oil supply passage 55 and the position of the oil passage 55f are disposed so as to overlap in the axial direction, and at an axial position including this overlap portion. An oil supply communication portion 91c that communicates the outlet of the oil passage 55g and the inlet of the oil passage 55f is continuously provided in the circumferential direction at the fitting portion between the outer peripheral surface of the turbine shaft 4 and the inner peripheral surface of the boss portion 6d. Is formed. The communication portion 91c for oil supply is disposed on the rear side (axial anti-torque converter side) from the communication portion 91a for oil discharge.

  Further, in the fitting portion between the outer peripheral surface of the turbine shaft 4 and the inner peripheral surface of the boss portion 6d, an internal pressure is provided on the front side of the oil discharge communicating portion 91a via the oil discharge passage 69 for the internal pressure chamber 34a. An internal pressure chamber communication portion 91b communicating with the chamber 34a is formed. In the internal pressure chamber communication portion 91b, a needle bearing 77 is interposed between the outer peripheral surface of the turbine shaft 4 and the inner peripheral surface of the boss portion 6d.

  In the fitting portion between the outer peripheral surface of the turbine shaft 4 and the inner peripheral surface of the boss portion 6d, the oil pressure communicating portion 91a is sandwiched between the inner pressure chamber communicating portion 91b and the front side (axial torque converter side). A first seal member 71 is provided, and a second seal member 72 is provided on the rear side (on the axial anti-torque converter side) to partition between the oil supply communication portion 91c and the rear of the oil supply communication portion 91c. A third seal member 73 is provided on the side (axial anti-torque converter side).

  Each of the seal members 71, 72, 73 is, for example, a metal C-shaped ring, and is attached to seal ring grooves 81, 82, 83 provided on the outer peripheral surface of the turbine shaft 4. The seal members 71, 72, 73 may rattle in the axial direction in the seal ring grooves 81, 82, 83 depending on the state of hydraulic pressure on both sides of the seal member. In this case, the sealing performance is impaired. There are concerns.

  In this regard, in the present embodiment, an internal pressure higher than the exhaust pressure from the cancel chamber 34c always acts on the internal pressure chamber communication portion 91b, and the lockup clutch 3f is engaged and slipped on the fuel supply communication portion 91c. During the control, a hydraulic pressure higher than the exhaust pressure from the cancel chamber 34c is applied. Therefore, during the engagement and slip control of the lock-up clutch 3f, the first seal member 71 and the second seal member 72 are brought closer to the oil draining communication portion 91a side in the seal ring grooves 81 and 82 due to the pressure difference. Thus, a good sealing property can be obtained for these sealing members 71 and 72.

  Further, during the engagement and slip control of the lock-up clutch 3f, a higher hydraulic pressure acts on the oil supply communication portion 91c than the rear side portion sandwiching the third seal member 73. Therefore, due to this pressure difference, the third seal member 73 is maintained in the seal ring groove 83 toward the rear side, so that the third seal member 73 can also have good sealing performance. As described above, since the sealing performance on both sides in the axial direction across the oil supply communication portion 91c is maintained well, the engagement hydraulic pressure of the lock-up clutch 3f can be accurately controlled, and slip control that requires particularly precise control. Can be performed satisfactorily.

  In the first embodiment, the configuration in which the oil discharge passage 65 for the cancel chamber 34c and the oil discharge passage 67 for the centrifugal balance chamber 29 are merged in the oil passage 65b formed in the boss portion 6d has been described. However, in the present invention, the drain side open end portion of the oil passage 65b is closed with a plug similar to the plug 37 provided in the oil passage 55b, so that both the oil discharge passages 65 and 67 are not merged. Also good.

[Second Embodiment]
A second embodiment of the present invention will be described with reference to FIG.

  The automatic transmission 1 according to the second embodiment is configured in the same manner as in the first embodiment except for the oil supply passage 55 for the hydraulic chamber 34b and the oil discharge passage 65 for the cancel chamber 34c of the torque converter 3. Yes. Accordingly, in FIG. 5, the same components as those of the first embodiment are denoted by the same reference numerals as those in FIGS. 3 and 4, and detailed description thereof is omitted.

  In the second embodiment, the oil supply passage 55 is provided so as to guide the fastening hydraulic pressure supplied from the oil pump 30 to the hydraulic chamber 34 b through the oil passage 55 h outside the pipe member 36 in the turbine shaft 4.

  Specifically, the oil supply passage 55 includes, in order from the upstream side, an oil passage 55b and an oil passage 55g provided on the peripheral wall of the boss portion 6d, as in the first embodiment, and a turbine as in the first embodiment. An oil passage 55f provided in the shaft 4, an oil passage 55a outside the pipe member 36 in the oil hole 35 of the turbine shaft 4 disposed so as to communicate with the oil passage 55f, and a downstream portion of the oil passage 55a And an oil passage 55i provided in the radial direction through the peripheral wall of the turbine shaft 4 and an oil provided in the radial direction through the peripheral wall of the turbine hub 33f so as to communicate with the oil passage 55i. A passage 55j and an oil passage 55k provided through the peripheral wall of the boss portion 33e of the front cover 33a in the radial direction so as to allow communication between the oil passage 55j and the hydraulic chamber 34b.

  A plurality of sets of the oil passages 65i and 65j communicating with each other are provided on the peripheral walls of the turbine hub 33f and the turbine shaft 4 at intervals in the circumferential direction.

  On the other hand, the oil discharge passage 65 is provided so as to guide the hydraulic oil in the cancel chamber 34 c to the transmission mechanism 5 side through the oil passage 65 j inside the pipe member 36 in the turbine shaft 4.

  Specifically, the oil drainage passage 65 is provided in the boss portion 33e so as to extend from the portion constituting the cancel chamber 34c on the outer peripheral surface of the boss portion 33e of the front cover 33a toward the inner peripheral side in order from the upstream side. An oil passage 65h, and a clearance 65i formed in the inner space of the boss portion 33e so as to communicate with the oil passage 65h, on the front side of the front end portion of the turbine shaft 4 and the turbine hub 33f, and the clearance 65i. The oil passage 65j formed on the inner side of the pipe member 36 so as to communicate with the oil passage 65j and the oil hole 35 of the turbine shaft 4 formed on the rear side of the rear end portion of the pipe member 36 so as to communicate with the oil passage 65j. A space 65k formed, an oil passage 65l provided in a radial direction through the peripheral wall of the turbine shaft 4 so as to communicate with the space 65k, and the oil An oil passage 65m provided through the output member 21 of the high clutch 20 in the radial direction so as to communicate with 65l, and the output member 11 of the low clutch 10 in the radial direction so as to communicate with the oil passage 65m. And an oil passage 65n provided therethrough.

  A plurality of the oil passages 65l in the peripheral wall of the turbine shaft 4 are provided at intervals in the circumferential direction. A plurality of oil passages 65m, 65n of the output members 11, 21 are also provided at intervals in the circumferential direction.

  Thus, since the oil drainage path 65 in the second embodiment is configured not to pass through the boss portion 6d where the centrifugal force does not act, by utilizing the centrifugal force due to the rotation of the turbine shaft 4 or the like, Smooth oil draining can be realized.

  The oil discharge port of the oil discharge passage 65 is constituted by the plurality of oil passages 65 n provided in the output member 11 of the low clutch 10. These oil discharge ports 65n are arranged offset to the rear side in the axial direction with respect to the low clutch 10 and the high clutch 20. Therefore, it is possible to prevent the oil drained from the oil drain port 65n from adhering to the friction plates 14 and 24 of the low clutch 10 and the high clutch 20. Therefore, an increase in rotational resistance due to the viscosity received by the friction plates 14 and 24 when the clutches 10 and 20 are released is suppressed, and thereby the driving loss of the turbine shaft 4 can be suppressed.

  Further, the oil discharge port 65n is disposed on the front side (torque converter side) with respect to any frictional engagement element other than the low clutch 10 and the high clutch 20 in the transmission mechanism 5 in the axial direction. Accordingly, also in the second embodiment, the oil discharge port 65n of the oil discharge passage 65 is disposed so as not to overlap with any frictional engagement elements constituting the speed change mechanism 5 in the axial direction. Also for the frictional engagement element, an increase in rotational resistance due to oil drained from the oil drain port 65n can be suppressed, and driving loss of the turbine shaft 4 can be suppressed.

  While the present invention has been described with reference to the above-described embodiments, the present invention is not limited to the above-described embodiments.

  For example, in the above-described embodiment, the case where the present invention is applied to the automatic transmission 1 having the structure described in the first and second embodiments has been described. However, the present invention is applied to an automatic transmission having any structure. can do.

  For example, the automatic transmission to which the present invention is applied differs from the above-described embodiment, and may be a vertical automatic transmission, or a low clutch (first clutch) 10 and a high clutch (second clutch). An automatic transmission that does not include one or both of 20 may be used.

  As described above, according to the present invention, when a cancel chamber is provided for suppressing a change in the fastening force of the piston portion of the lockup clutch due to a change in the internal pressure of the torque converter, Since it becomes possible to suppress the driving loss due to the oil drainage, there is a possibility that it can be suitably used in the technical field of manufacturing this type of automatic transmission or a vehicle equipped with the automatic transmission.

DESCRIPTION OF SYMBOLS 1 Automatic transmission 2 Engine output shaft 3 Torque converter 3f Lock-up clutch 4 Turbine shaft 5 Transmission mechanism 6 Transmission case 6b Pump storage wall (partition wall)
6d Boss part 10 1st clutch (low clutch)
11 Output member 14 Friction plate 20 Second clutch (high clutch)
21 Output member 24 Friction plate 29 Centrifugal balance chamber 30 Oil pump 33a Front cover 33b Pump shell 33c Lock-up piston (piston part)
33d Seal plate 34a Torque converter internal pressure chamber 34b Hydraulic chamber 34c Cancel chamber 35 Oil hole 36 Pipe member 39 Restriction 55 Oil supply passage for hydraulic chamber 55f Second oil passage 55g Fourth oil passage 65 Drain oil passage 65b Cancel chamber Oil passage 65f first oil passage 65g third oil passage 65n oil discharge port 66 oil discharge port 67 for the centrifugal balance chamber Oil discharge passage 71 First seal member 72 Second seal member 73 Third seal member 81, 82, 83 Seal ring groove 91a Oil discharge communication portion 91b Internal pressure chamber communication portion 91c Oil supply communication portion

Claims (4)

A torque converter;
A transmission mechanism in which the output of the torque converter is input via a turbine shaft;
The torque converter includes a lock-up clutch that connects an input side and an output side thereof,
An automatic transmission provided in the torque converter with a hydraulic chamber to which a fastening hydraulic pressure is supplied across a piston portion of the lockup clutch and a cancel chamber communicated with the torque converter internal pressure chamber via a throttle. There,
An oil discharge passage for the cancel chamber is provided that guides the hydraulic oil in the cancel chamber to the transmission mechanism side through the turbine shaft.
The automatic transmission according to claim 1, wherein the oil discharge port of the oil discharge passage for the cancel chamber is provided at a position in the axial direction so as not to overlap with a frictional engagement element constituting the transmission mechanism. The transmission mechanism includes a frictional engagement element including a centrifugal balance chamber that axially overlaps the turbine shaft,
The drainage passage for the centrifugal balance chamber that discharges hydraulic oil from the centrifugal balance chamber is formed so as to join the drainage passage for the cancellation chamber and communicate with the drainage port. Item 2. The automatic transmission according to Item 1. In the transmission case, a partition wall that partitions the accommodating portion of the torque converter and the accommodating portion of the transmission mechanism is provided,
A boss portion through which the turbine shaft passes is provided in the partition wall so as to extend in the axial direction toward the speed change mechanism,
One oil hole formed in the peripheral wall of the boss portion constitutes an oil passage from the junction of the oil discharge passage for the cancellation chamber and the oil discharge passage for the centrifugal balance chamber toward the oil discharge port. The automatic transmission according to claim 2, wherein the automatic transmission is provided. In the turbine shaft, a first oil passage that constitutes an oil discharge passage for the cancellation chamber, and a second oil passage that constitutes an oil supply passage that supplies fastening hydraulic pressure to the hydraulic chamber are provided,
In the peripheral wall of the boss portion, a third oil passage that constitutes a downstream portion of the oil discharge passage for the cancel chamber from the first oil passage, and an upstream portion of the second oil passage in the oil supply passage. A fourth oil passage is provided,
On the outer peripheral surface of the turbine shaft, an outlet of the first oil passage and an inlet of the second oil passage are provided,
On the inner peripheral surface of the boss portion, an inlet of the third oil passage and an outlet of the fourth oil passage are provided,
In the fitting portion between the outer peripheral surface of the turbine shaft and the inner peripheral surface of the boss portion, an axial torque is interposed across an oil discharge communicating portion that communicates the outlet of the first oil passage and the inlet of the third oil passage. A first seal member that partitions the converter side from the internal pressure chamber communicating portion that communicates with the internal pressure chamber of the torque converter includes an outlet of the fourth oil passage and an inlet of the second oil passage on the axial anti-torque converter side. 4. The automatic transmission according to claim 3, wherein the second seal members that partition between the communicating portions for oil supply to be communicated are mounted in seal ring grooves provided on the outer peripheral surface of the turbine shaft. 5.

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