JP2007263155A - Automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an automatic transmission having compact construction while reliably maintaining the functions of a clutch and a brake. <P>SOLUTION: The automatic transmission comprises a ring-shaped first member 40 having a hub member 22 on the inner periphery side of 35RCL 16 and a hub member 31 on the inner periphery side of 26Brk 19, both of which are formed in one unit, and a disc-shaped second member 41 whose radial outer end portion is joined to the first member 40 and whose radial inner end portion is joined to a sun gear 12a of a third planetary gear mechanism 12. The plate thickness of the first member 40 is smaller than the plate thickness of the second member 41. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an automatic transmission, and more particularly to an improved member for linking a predetermined clutch, brake, and planetary gear mechanism.

  Conventionally, as an automatic transmission installed in a vehicle such as an automobile, a constant reduction planetary gear mechanism that constantly reduces the rotation input from the input shaft to the ring gear (input unit), and another planet adjacent to the constant reduction planetary gear mechanism. An annular clutch having a multi-plate friction plate that connects and separates a pinion carrier (output part) of a pinion of a constant speed planetary gear mechanism and a sun gear (input part) of another planetary gear mechanism, and other planetary gear mechanisms One having an annular brake having a multi-plate friction plate for connecting and separating the sun gear and the transmission case is well known (for example, see Patent Documents 1 and 2).

  In the automatic transmission having these configurations, the applicant of the present application makes the other planetary gear mechanism adjacent to the always-reducing planetary gear mechanism in the axial direction and the multi-plate friction plate of the clutch on the radially outer side of the always-reducing planetary gear mechanism. And a brake with a multi-plate friction plate on the outside in the radial direction of the clutch is being put into practical use. In this automatic transmission, the drum member on the outer peripheral side of the clutch is always connected to the pinion carrier of the reduction planetary gear mechanism, and the hub member on the inner peripheral side of the clutch and the hub member on the inner peripheral side of the brake are connected to the other planetary gear mechanism. It is connected to the sun gear. The drum member of the clutch and the other member are opposed to each other in the axial direction, and the disc portion of the connecting member that connects the hub member of the brake and the sun gear of the other planetary gear mechanism passes through the gap therebetween. ing.

JP 2003-278797 A JP 2003-287111 A

  Another planetary gear mechanism is axially adjacent to the constant reduction planetary gear mechanism, a multi-plate friction plate of the clutch is provided on the radially outer side of the constant reduction planetary gear mechanism, and a multi-plate friction plate of the brake is provided on the radially outer side of the clutch. In the provided automatic transmission, it is possible to integrally form a clutch hub member, a brake hub member, and a connecting member for connecting these to a sun gear of another planetary gear mechanism. However, this integral member does not contribute to downsizing of the automatic transmission because it is necessary to increase the overall thickness in order to withstand the load stress caused by the operation of the clutch and brake.

  In particular, when the drum member of the clutch and the other member face each other in the axial direction, the disc portion of the integral member passes through the gap therebetween, and the disc portion and the drum member and the other member It is necessary to provide a certain clearance between them, and if the thickness of the disk portion of the integrated member increases, the interval between the drum member and the other member must be increased, so the axial size of the automatic transmission is compact. Hinders Moreover, since this integral member is cast-molded, it is disadvantageous in terms of production cost.

  Therefore, the clutch hub member and the connecting member are integrally formed, and the brake hub member is joined to the integrated member, or the brake hub member and the connecting member are integrally formed, and the clutch hub member is attached to the integrated member. A joining structure is conceivable. However, in the former case, the strength of the integrated member is reduced by joining with the brake hub member, and in the latter case, the disk portion having a large plate thickness of the integrated member passes between the drum member and the other member. As described above, problems such as hindering the downsizing of the automatic transmission in the axial direction occur.

  It is an object of the present invention to provide a disk-shaped first member in which a radially inner end portion is joined to an input portion of a planetary gear mechanism on an annular first member in which a hub member of a clutch and a hub member of a brake are integrally formed. It is an object of the present invention to provide an automatic transmission in which the functions of a clutch and a brake can be reliably maintained and compactness can be achieved by joining the radially outer end portions of two members.

  According to another aspect of the present invention, an automatic transmission planetary gear mechanism that constantly reduces the rotation input to the input unit, another planetary gear mechanism that is axially adjacent to the constant reduction planetary gear mechanism, and a constant reduction planetary gear. An annular clutch having a multi-plate friction plate for connecting and separating the output portion of the gear mechanism and the input portion of another planetary gear mechanism, and multi-plate friction for connecting and separating the input portion of the other planetary gear mechanism and the transmission case An automatic transmission including an annular brake having a plate, and an annular first member integrally formed with an inner peripheral hub member of the clutch and an inner peripheral hub member of the brake; A disk-shaped second member having a radially outer end portion joined to the first member and a radially inner end portion joined to an input portion of another planetary gear mechanism; and the thickness of the first member is The thickness is smaller than the thickness of the second member.

  In this automatic transmission, a hub member on the inner peripheral side of the clutch and a hub member on the inner peripheral side of the brake are integrally formed on the annular first member, and the radially outer end portion of the disk-shaped second member is It is joined to the first member, and the radially inner end portion of the second member is joined to the input part of another planetary gear mechanism. The load stress due to the operation of the clutch and brake is greater in the second member than in the first member. Therefore, the plate thickness of the first member is made smaller than the plate thickness of the second member. The function of can be maintained reliably. The automatic transmission can be made compact by making the plate thickness of the first member smaller than the plate thickness of the second member.

The following configuration can be adopted in the invention of claim 1.
A radially outer end portion of the second member is joined to a portion of the first member that is located radially inward of the outer peripheral drum member of the clutch. The clutch and the brake are disposed so as to overlap in the axial direction, and the first member is formed in a U-shaped cross section (Claim 3).

  The first member and the always-reducing planetary gear mechanism are disposed so as to overlap in the axial direction. A plurality of planetary gear mechanisms including the always-reducing planetary gear mechanism and another planetary gear mechanism, wherein the always-reducing planetary gear mechanism is concentric with the input shaft and is most distant from the engine among the plurality of planetary gear mechanisms. (Claim 5). The piston member of the clutch and the piston member of the brake are disposed so as to overlap in the axial direction.

  According to the automatic transmission of claim 1, the automatic transmission includes a constant reduction planetary gear mechanism, another planetary gear mechanism, a clutch, and a brake, and the hub member on the inner peripheral side of the clutch and the hub member on the inner peripheral side of the brake are integrated. A disk-shaped second member having a radially outer end portion joined to the first member and a radially inner end portion joined to an input portion of another planetary gear mechanism; Therefore, the load stress due to the operation of the clutch and brake is greater in the second member than in the first member, but the plate thickness of the first member is smaller than the plate thickness of the second member, The functions of the clutch and brake can be maintained reliably, the automatic transmission can be made compact in the axial direction, and the automatic transmission can be expected to be reduced in the radial direction. Since each member can be press-molded, there is a manufacturing cost. To become.

  According to the automatic transmission of the second aspect, since the radially outer end portion of the second member is joined to the portion located on the radially inner side of the drum member on the outer peripheral side of the clutch in the first member, the plate thickness is Since the small first member is disposed so as to pass between the drum member of the clutch and the other member facing the drum member in the axial direction, the gap between the drum member and the other member can be reduced. The axial direction of the automatic transmission can be made compact.

  According to the automatic transmission of the third aspect, since the clutch and the brake are disposed so as to overlap in the axial direction and the first member is formed in a U-shaped cross section, the axial direction and the radial direction of the clutch and the brake are arranged. Compactness can be achieved, and the strength of the first member can be increased to increase reliability.

  According to the automatic transmission of the fourth aspect, since the first member and the always-reducing planetary gear mechanism are disposed so as to overlap in the axial direction, the clutch, the brake, and the always-reducing planetary gear mechanism can be made compact in the axial direction. Can be planned.

  According to the automatic transmission of claim 5, a plurality of planetary gear mechanisms including a constant reduction planetary gear mechanism and another planetary gear mechanism are provided, and the constant reduction planetary gear mechanism is concentric with the input shaft and a plurality of planetary gear mechanisms. Since the gear mechanism is disposed at the position farthest from the engine, the member layout on the side away from the engine of the automatic transmission can be made compact.

  According to the automatic transmission of the sixth aspect, since the piston member of the clutch and the piston member of the brake are disposed so as to overlap in the axial direction, the clutch and the brake including the piston member can be made compact in the axial direction. be able to.

  The automatic transmission according to the present invention includes an always-reducing planetary gear mechanism that constantly decelerates rotation input to the input unit, another planetary gear mechanism that is axially adjacent to the always-reducing planetary gear mechanism, and an output of the always-reducing planetary gear mechanism. And an annular clutch having a multi-plate friction plate for connecting and separating the input portion of the other planetary gear mechanism, and an annular clutch having a multi-plate friction plate for connecting and separating the input portion of the other planetary gear mechanism and the transmission case. An annular first member in which a hub member on the inner peripheral side of the brake and the clutch and a hub member on the inner peripheral side of the brake are integrally formed, a radially outer end portion joined to the first member, and another planetary gear A disk-shaped second member having a radially inner end joined to the input portion of the mechanism is provided.

  As shown in FIGS. 1 and 3, an automatic transmission 1 mounted on a vehicle such as an automobile includes an input shaft 2 to which engine output is input, an output gear 3 that outputs driving force to the wheels, and these A transmission mechanism 4 interposed between the input shaft 2 and the output gear 3 and a transmission case 5 for housing the transmission mechanism 4 are provided.

  The transmission mechanism 4 includes first to fourth planetary gear mechanisms 10 to 13, LCL14 (low clutch), HCL15 (high clutch), 35RCL16 (35 reverse clutch), OWCL17 (one-way clutch), LRBrk18 (low reverse brake), 26Brk19 (26 brakes).

  In the first planetary gear mechanism 10, the sun gear 10 a is fixed to the transmission case 5, the pinion carrier 10 c of the pinion 10 b is connected to the clutch drum 14 a on the outer peripheral side of the LCL 14, and the ring gear 10 d is connected to the outer peripheral side of the input shaft 2 and the HCL 15. It is connected to the clutch drum 15a.

  In the second planetary gear mechanism 11, the sun gear 11a is connected to the clutch hub 14b on the inner peripheral side of the LCL 14, the pinion carrier 11c of the pinion 11b is connected to the output gear 3 and the ring gear 12d of the third planetary gear mechanism 12, and the ring gear 11d. Is connected to the hub member 18a on the inner peripheral side of the LRBrk 18, and the OWCL 17 is interposed between the hub member 18a (ring gear 11d) and the transmission case 5.

  In the third planetary gear mechanism 12, the sun gear 12a is connected to the brake hub 19a on the inner peripheral side of 26Brk19 and the clutch hub 16b on the inner peripheral side of 35RCL16, and the pinion carrier 12c of the pinion 12b is connected to the hub member 18a of the LRBrk18 and the HCL15. It is connected to the circumferential clutch hub 15b.

  In the fourth planetary gear mechanism 13, the sun gear 13 a is fixed to the transmission case 5, the pinion carrier 13 c of the pinion 13 b is connected to the clutch drum 16 a on the outer peripheral side of the 35 RCL 16, and the ring gear 13 d is connected to the input shaft 2.

  LCL14, HCL15, 35RCL16, LRBrk18, and 26Brk19 are controlled by a control device such as an ECU, respectively, so that the gear position of the transmission mechanism 4 is selectively switched to any one of the first to sixth gears and the reverse gear. FIG. 2 shows the states of LCL14, HCL15, 35RCL16, LRBrk18, 26Brk19, and OWCL17 at each gear position, and “◯” indicates the engaged state. Note that the OWCL 17 in the first speed is engaged only when accelerating, and the LRBrk 18 is engaged only when engine braking such as manual mode is required.

  Next, the third planetary gear mechanism 12, the fourth planetary gear mechanism 13, 35RCL16, 26Brk19, etc. will be described in detail. The direction of arrow a in FIG. 3 is the axial direction, and the right side of FIG.

  As shown in FIG. 3, the fourth planetary gear mechanism 13 is a constant reduction planetary gear mechanism that constantly decelerates rotation input from the input shaft 2 to the ring gear 13 d that is an input unit, and is concentric with the input shaft 2 and The third planetary gear mechanism 12, which is disposed at the rearmost position farthest from the engine among the first to fourth planetary gear mechanisms 10 to 13 and corresponds to the other planetary gear mechanisms, is concentric with the input shaft 2. In addition, the fourth planetary gear mechanism 13 is disposed adjacent to the front side in the axial direction.

  Here, the transmission case 5 includes a case body 5a that is open rearward and a case cover 5b that closes the rear end of the case body 5a. The case cover 5b includes a rear wall portion 5c, a rear wall portion 5c, and the like. And a boss portion 5d formed in a forward projecting shape at the center portion. A rear end portion of the input shaft 2 is rotatably accommodated in the boss portion 5d, and a sleeve 50 is spline-coupled to the boss portion 5d in an outer fitting shape.

  In the fourth planetary gear mechanism 13, the sun gear 13a is splined to the sleeve 50 so as to be externally fitted, and the radially inner end of the pinion carrier 13c located on the rear side of the pinion 13b is rotatably fitted to the sleeve 50. The cylindrical member 51 is spline-coupled to the front end portion, the radial outer end portion of the disk member 52 is joined to the front end portion of the ring gear 13d, and the radial inner end portion of the disk member 52 is spline-coupled to the input shaft 2. .

  The 35 RCL 16 is formed in an annular shape, and includes a multi-plate friction member 20, an outer drum member 21 (clutch drum 16 a), an inner hub member 22 (clutch hub 16 b), a piston member 23, and a return spring 24. And a pin retainer 13c that is an output part of the fourth planetary gear mechanism 13 and a sun gear 12a that is an input part of the third planetary gear mechanism 12 are connected and separated.

  The multi-plate friction member 20 is disposed on the outer side in the radial direction of the fourth planetary gear mechanism 13, and between the drum member 21 and the hub member 22, a plurality of (for example, four) annular disks 20 a and a plurality of (for example, three) A plurality of annular plates 20b are alternately arranged in the axial direction, and a plurality of annular discs 20a are spline-coupled to the drum member 21 so that the annular disc 20a located at the front end moves forward. A plurality of annular plates 20b are spline-coupled to the hub member 22 so as to be fitted by the stop ring 20c.

  The drum member 21 is formed in a concave shape that is recessed from the front to the rear, and a plurality of annular discs 20a are splined to the front half, and inclined toward the axial center from the front half to the rear. 5 b is disposed along the rear wall portion 5 c, and the radially inner end portion is joined to the rear end portion of the cylindrical member 51.

  The piston member 23 is disposed along the inner side of the drum member 21 and is formed in a stepped concave shape that is recessed from the front to the rear, and the cylindrical portion of the radially inner end is oiled in the cylindrical member 51 in the axial direction. It is fitted externally so that it can slide freely. A spring retainer 25 is disposed on the front side of the radially inner portion of the piston member 23, and the spring retainer 25 is externally fitted to the tubular member 51 to restrict forward movement. The return spring 24 is disposed between the piston member 23 and the spring retainer 25 and urges the piston member 23 rearward.

  An oil chamber 26 is formed between the piston member 23 and the drum member 21, and when oil pressure is supplied to the oil chamber 26 from an oil passage 26 a formed in the transmission case 5, the sleeve 50, and the cylindrical member 51, the piston The member 23 is driven forward against the urging force of the return spring 24, and the multi-plate friction member 20 is pressed forward and connected by the radially outer end portion of the piston member 23. When the hydraulic pressure in the oil chamber 26 is released, the piston member 23 is returned to the retracted position by the return spring 24, and the multi-plate friction member 20 is separated.

  A centrifugal balance chamber 27 is formed between the piston member 23 in which the return spring 24 is accommodated and the spring retainer 25, and the centrifugal balance chamber 27 has an oil passage 27 a formed in the transmission case 5, the sleeve 50, and the cylindrical member 51. Lubricating oil can be supplied from The piston member 23, the oil chamber 26, the centrifugal balance chamber 27, and the like rotate integrally with the drum member 21, but the hydraulic pressure on the oil chamber 26 side and the hydraulic pressure on the centrifugal balance chamber 27 side generated by the rotation are cancelled.

  26Brk19 is formed in an annular shape, and includes a multi-plate friction member 30, an inner peripheral hub member 31 (brake hub 19a), a piston member 32, a return spring 33, and a spring retainer 34, and is a third planet. The sun gear 12a, which is the input portion of the gear mechanism 12, and the transmission case 5 are connected and separated.

  The multi-plate friction member 30 is disposed radially outside the multi-plate friction member 20 of the 35 RCL 16, and a plurality of (for example, five) annular disks 30 a and a plurality of (for example, five) are disposed between the transmission case 5 and the hub member 31. Four annular plates 30b are alternately arranged in the axial direction, and a plurality of annular discs 30a are spline-coupled to the transmission case 5 so as to be fitted forward to the annular disc 30a located at the front end. The movement is restricted by the locking ring 30c, and the plurality of annular plates 30b are splined to the hub member 31 in an outer fitting manner.

  The piston member 32 is disposed on the rear side of the piston member 23 of the 35RCL 16 on the rear side of the multi-plate friction member 30, is formed in a ring shape, and has a front open concave groove 5e formed in the case cover 5b. Are fitted in an oil-tight slidable manner in the axial direction. A spring retainer 34 is disposed on the radially inner side of the output portion 32a of the piston member 32, and the rear end portion of the spring retainer 34 is fixed to the case cover 5b. The return spring 33 is reduced in diameter toward the rear and is disposed between the piston member 32 and the spring retainer 34 to urge the piston member 32 rearward.

  An oil chamber 35 is formed between the piston member 32 and the case cover 5 b. When hydraulic pressure is supplied to the oil chamber 35 from an oil passage 35 a formed in the transmission case 5, the piston member 32 is connected to the return spring 33. Driven forward against the urging force, the multi-plate friction member 30 is pushed forward by the output portion 32a of the piston member 32 and connected. When the oil pressure in the oil chamber 35 is released, the piston member 32 is returned to the retracted position by the return spring 33, and the multi-plate friction member 30 is separated.

  Here, the annular first member 40 in which the hub member 22 on the inner peripheral side of the 35 RCL 16 and the hub member 31 on the inner peripheral side of 26 Brk 19 are integrally formed, and the radially outer end portion of the first member 40 has a radial outer end portion. A disk-shaped second member 41 joined to the sun gear 12a, which is joined and input to the third planetary gear mechanism 12, is joined to the sun gear 12a. The first and second members 40, 41 are respectively The first member 40 is formed by press molding so that the plate thickness (for example, 2 mm) is smaller than the plate thickness (for example, 3.2 mm) of the second member 41.

  The first member 40 is formed in a U-shaped cross-section with an opening at the front, and its inner peripheral wall portion 40a is formed on the hub member 22 of the 35RCL16, and is disposed near the radially outer side of the ring gear 13d of the fourth planetary gear mechanism 13. The outer peripheral wall portion 40b is formed in the hub member 31 of 26Brk19 and is disposed in the vicinity of the radially outer side of the drum member 21 of 35RCL16.

  Here, the front end portion of the drum member 21 of the 35 RCL 16 faces the rear end portion of the hub member 18a of the LRBrk 18 from the rear side, and the first member 40 has a vertical plate portion 40c between the drum member 21 and the hub member 18a. It is arrange | positioned so that it may pass. The radially outer end portion of the second member 41 is joined by spot welding or seam welding to the rear surface portion of the vertical plate portion 40c located on the radially inner side of the drum member 21 of the 35RCL16 in the first member 40. Has been.

The automatic transmission 1 described above has the following effects.
An annular first member 40 in which a hub member 22 on the inner peripheral side of 35 RCL 16 and a hub member 31 on the inner peripheral side of 26 Brk 19 are integrally formed, and a radially outer end portion is joined to the first member 40 and Since the disk-shaped second member 41 whose inner end in the radial direction is joined to the sun gear 12 a of the third planetary gear mechanism 12 is provided, the load stress due to the operation of the 35 RCL 16 and 26 Brk 19 is second than that of the first member 40. The member 41 acts more greatly, but the plate thickness of the first member 40 is made smaller than the plate thickness of the second member 41 to reliably maintain the functions of the 35RCL16 and 26Brk19, and the axial direction of the automatic transmission 1 The automatic transmission 1 can be made compact in the radial direction, and the first and second members 40 and 41 can be press-molded, which is advantageous in terms of production cost. Nina .

  Since the radially outer end portion of the second member 40 is joined to a portion of the first member 40 located on the radially inner side of the outer peripheral drum member 21 of the 35 RCL 16, the first member 40 having a small plate thickness is attached to the 35 RCL 16. Since the drum member 21 is disposed so as to pass between the drum member 21 and the hub member 18a of the LRBrk 18 facing the drum member 21 in the axial direction, the gap between the drum member 21 and the hub member 18a can be reduced. The machine 1 can be made compact in the axial direction.

  35RCL16 and 26Brk19 are disposed so as to overlap in the axial direction, and the first member 40 is formed in a U-shaped cross section, so that the 35RCL16 and 26Brk19 can be made compact in the axial direction and the radial direction. Since the first member 40 and the fourth planetary gear mechanism 13 are arranged so as to overlap in the axial direction by increasing the strength of the 40, the axial direction of the 35RCL16 and 26Brk19 and the fourth planetary gear mechanism 13 is increased. Compactness can be achieved.

  Since the fourth planetary gear mechanism 13 is disposed concentrically with the input shaft 2 and at a position farthest from the engine among the first to fourth planetary gear mechanisms 10 to 13, the engine of the automatic transmission 1 is Since the member layout on the separated side can be made compact and the piston member 23 of 35RCL16 and the piston member 32 of 26Brk19 are arranged to overlap in the axial direction, 35RCL16 including the piston members 23 and 32 respectively. 26Brk19 can be made compact in the axial direction.

  It should be noted that various modifications other than those disclosed above can be made without departing from the spirit of the present invention, and the present invention can be applied to various automatic transmissions.

1 is a skeleton diagram schematically showing an automatic transmission according to an embodiment. FIG. It is a chart which shows the state of a plurality of friction engaging elements about a plurality of gear stages of a speed change mechanism. It is a longitudinal cross-sectional view of the principal part of an automatic transmission.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Automatic transmission 2 Input shaft 5 Transmission case 10-13 1st-4th planetary gear mechanism 12a Sun gear 13c Pinion carrier 13d Ring gear 16 35RCL
19 26 Brk
20, 30 Multi-plate friction plate 21 Drum member 22, 31 Hub member 23, 32 Piston member 40 First member 41 Second member

Claims (6)

An always-reducing planetary gear mechanism that constantly decelerates rotation input to the input unit, another planetary gear mechanism that is axially adjacent to this always-reducing planetary gear mechanism, an output unit of the always-reducing planetary gear mechanism, and other planets An annular clutch having a multi-plate friction plate for connecting and separating the input portion of the gear mechanism, and an annular brake having a multi-plate friction plate for connecting and separating the input portion of the other planetary gear mechanism and the transmission case. Automatic transmission,
An annular first member in which a hub member on the inner peripheral side of the clutch and a hub member on the inner peripheral side of the brake are integrally formed, a radially outer end portion is joined to the first member, and another planet A disk-shaped second member having a radially inner end joined to the input portion of the gear mechanism,
An automatic transmission characterized in that the plate thickness of the first member is smaller than the plate thickness of the second member.   An automatic transmission characterized in that a radially outer end portion of a second member is joined to a portion of the first member located radially inward of a drum member on the outer peripheral side of the clutch.   The automatic transmission according to claim 1 or 2, wherein the clutch and the brake are disposed so as to overlap in the axial direction, and the first member is formed in a U-shaped cross section.   The automatic transmission according to any one of claims 1 to 3, wherein the first member and the constant reduction planetary gear mechanism are disposed so as to overlap in the axial direction. A plurality of planetary gear mechanisms including the normally reduced planetary gear mechanism and other planetary gear mechanisms;
The said always-reducing planetary gear mechanism is arrange | positioned in the position which is concentrically with an input shaft and the most distant from the engine among several planetary gear mechanisms. Automatic transmission. 6. The automatic transmission according to claim 1, wherein the piston member of the clutch and the piston member of the brake are disposed so as to overlap in the axial direction.