JP2005233392A - Automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide the automatic transmission which constrains enlargement of dimension in axial direction of the automatic transmission and a hydraulic control unit, and at the same time enhances shift quality without providing new control sequence. <P>SOLUTION: In the automatic transmission, a simple planetary gear mechanism 20 and a ravigneaux planetary gear mechanism 60 are adjacently disposed within a transmission case 100 via a first drum clutch 30, a first ravigneaux planetary sun gear 40<SB>s1</SB>is coupled to a simple planetary gear carrier 20c for driving via a first clutch 30, and at the same time a second drum clutch 40 is disposed within a clutch 30, and a second ravigneaux planetary sun gear 60<SB>s2</SB>is coupled to the simple planetary carrier 20c for driving via the second clutch 40. The carrier 20c is coupled to the sun gear 60<SB>s2</SB>for driving by a first one-way clutch C1 while the sun gear 60<SB>s2</SB>is connected to a first brake 70 via a second one-way clutch C2. A second brake 80 and a third one-way clutch C3 are arranged in the vicinity of outer periphery of a ravigneaux planetary carrier 60c, and the second clutch C2 is disposed in a space surrounded by the first clutch C1, the first brake 70 and the third clutch C3. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an automatic transmission in which a simple planetary gear mechanism and a Ravigneaux type planetary gear mechanism are drive-coupled in a transmission case via at least two drum clutches, and a one-way clutch is provided as a countermeasure for a shift shock.

  As shown in the schematic cross-sectional view of FIG. 10, a conventional automatic transmission having a one-way clutch includes a simple planetary gear mechanism 2 disposed in front and rear in a transmission case 100 in an FR (engine front and rear wheel drive) vehicle. In addition, there is one in which a Ravigneaux type planetary gear mechanism 6 is drive-coupled via two drum clutches 3 and 4 (see, for example, Patent Document 1).

JP 2000-199548 A

10 will be described in detail. The simple planetary gear mechanism 2 uses the ring gear 2r coupled to the input shaft 1 as an input and outputs the carrier 2c via the sun gear 2s fixed to the transmission case 100. The first sun gear 6s ₁ of the Ravigneaux type planetary gear mechanism 6 is drive-coupled to the carrier 2c via the first drum clutch 3, and the first sun gear 6s ₁ and the first drum clutch 3 are connected to the carrier 2c by a band brake B. The first sun gear 6 s ₁ is also connected to a multi-plate brake 7 that causes braking on the transmission case 100 via a one-way clutch Co. Further, in the first drum clutch 3, a second drum clutch 4 that is engaged with the first drum clutch 3 via the carrier 2c of the simple planetary gear mechanism 2 is disposed. The second sun gear 6 s ₂ of the Ravigneaux type planetary gear mechanism 6 is drivingly coupled via the second drum clutch 4.

  By the way, it is preferable to reduce the number of one-way clutches to be used as much as possible considering the increase in weight and the occurrence of friction, but it also has an excellent function in that it is easy to take measures to reduce shift shock. It is a fact. For this reason, it is also a fact that it is necessary to use a one-way clutch when it is intended to provide an automatic transmission that can easily take measures against shift shock.

However, in the automatic transmission as described above, in order to ensure power transmission between the simple planetary gear mechanism and the Ravigneaux type planetary gear mechanism, the carrier of the simple planetary gear mechanism 2 as shown in region X of FIG. 2c is drivingly coupled to the first sun gear 6s ₁ of the Ravigneaux type planetary gear mechanism 6 via the first drum clutch 3, and the first sun gear 6s ₁ is connected to the multi-plate brake 7 via the one-way clutch Co. Therefore, when a new one-way clutch is required, the axial dimension of the automatic transmission becomes long unless the one-way clutch is arranged at an appropriate position.

  In addition, since there is a demand for multi-stage automatic transmissions, the conventional forward 4-speed or 5-speed automatic transmission is shifting to a forward 6-speed automatic transmission. As the number of stages increases, switching control between the clutches becomes complicated, and the valves and hydraulic circuits of the hydraulic control device that control the clutch become complicated, resulting in a longer hydraulic control device and a new control sequence. There must be.

  In addition, in the forward 6-speed automatic transmission, the timing of the release of the first drum clutch and the engagement of the second drum clutch, which are switched during the downshift from the 5th speed to the 4th speed, is driven down and coasted down. It is necessary to improve the shift quality by suppressing the shock caused by switching between the clutches to a low level by properly performing the driving conditions.

  The problem to be solved by the present invention has been made in view of the above-mentioned facts, and it is possible to suppress an increase in the axial dimension of an automatic transmission and a hydraulic control device, and to achieve shift quality without providing a new control sequence. An object of the present invention is to provide an automatic transmission capable of improving the speed.

  For this reason, the invention according to claim 1 includes an input unit that inputs rotation from a drive source, an output unit that outputs a rotated rotation, and a plurality of connecting members that integrally connect a plurality of rotating elements. Four clutches that are arranged between the input part, the output part, the connecting member, and the rotating elements of the two sets of planetary gears, and selectively connect / disconnect, and three brakes that selectively fix, An automatic transmission gear transmission having shift control means for obtaining at least six forward speeds and one reverse speed by appropriately engaging and releasing three brakes, wherein the two planetary gears are simple planetary gear mechanisms. And a Ravigneaux type planetary gear mechanism, wherein the simple planetary gear mechanism is a speed reducer that constantly decelerates the input rotation of the input unit, and the Ravigneaux type planetary gear mechanism has two sets of a first sun gear and a second sun gear. A Ravigneaux type planetary gear mechanism comprising: a ring gear, a short pinion that meshes with the first sun gear, a long pinion that meshes with the second sun gear, a carrier that integrally supports the short pinion and the long pinion, and a ring gear that meshes with the short pinion A first clutch having a first connecting member for integrally connecting the carrier of the simple planetary gear mechanism and the first sun gear of the Ravigneaux type planetary gear mechanism; the carrier of the simple planetary gear mechanism and the Ravigneaux type planetary gear mechanism; An automatic transmission having a third clutch having a second coupling member that integrally couples the second sun gear, wherein a third coupling member is provided in parallel with the second coupling member, Carrier of simple planetary gear mechanism and second sun of Ravigneaux type planetary gear mechanism A a is characterized in that it has been configured by the second clutch and the first one-way clutch of two sets of clutches for connecting together.

  According to a second aspect of the present invention, in the first aspect of the invention, a first clutch is provided for connecting the carrier of the simple planetary gear mechanism and the first sun gear of the Ravigneaux type planetary gear mechanism, and the first connecting member is The first clutch and the second one-way clutch are used.

  The invention according to claim 3 is the invention according to claim 2, wherein the second one-way clutch is connected to a fixing member by a first brake.

  The invention according to claim 4 is the invention according to any one of claims 1 to 3, wherein a fourth connecting member for integrally connecting the carrier and the fixing member of the Ravigneaux type planetary gear mechanism is provided. The connecting member is composed of a second brake and a third one-way clutch, the simple planetary gear mechanism and the Ravigneaux type planetary gear mechanism are arranged adjacent to each other, and the first one-way clutch, the second one-way clutch, and the third one-way clutch are the simple planetary gears. The gear mechanism and the Ravigneaux type planetary gear mechanism are arranged on the outer peripheral side within the axial dimension.

  According to a fifth aspect of the present invention, in the fourth aspect, the first one-way clutch and the second one-way clutch are arranged on an outer peripheral side within an axial dimension of the simple planetary gear mechanism, and the third one-way clutch is a Ravigneaux type planet. It arrange | positions to the outer peripheral side within the axial dimension of a gear mechanism.

  The invention according to claim 6 is the invention according to any one of claims 1 to 5, further comprising a fourth clutch that integrally connects the carrier and the input portion of the Ravigneaux type planetary gear mechanism. The one one-way clutch and the second one-way clutch are arranged on the outer peripheral side within the axial dimension of the simple planetary gear mechanism, and the third one-way clutch is arranged on the outer peripheral side within the axial dimension of the Ravigneaux type planetary gear mechanism. The gear mechanism and the Ravigneaux type planetary gear mechanism are characterized in that the fourth clutch is disposed on one side adjacent to each other and the first clutch, the second clutch, and the third clutch are disposed on the other side.

  An invention according to claim 7 is the invention according to any one of claims 1 to 6, further comprising a fourth clutch that integrally connects the carrier and the input part of the Ravigneaux type planetary gear mechanism, The second one-way clutch is arranged on the outer peripheral side within the axial dimension of the simple planetary gear mechanism, and the third one-way clutch is arranged on the outer peripheral side within the axial dimension of the Ravigneaux type planetary gear mechanism, and the simple planetary gear mechanism and the Ravigneaux type are arranged. In the planetary gear mechanism, the fourth clutch and the output unit are arranged on one side where the planetary gear mechanism is connected, and the first clutch, the second clutch, the third clutch, and the band brake are arranged on the other side. 3 clutches, 2nd clutches, 1st clutches are arranged, and the 1st clutch, 2nd clutch, 3rd clutch constituting the 1st clutch, 2nd clutch, 3rd clutch in the axial range Clutch, in which they are arranged such that the clutch plate of the third clutch overlap, in addition, characterized in that a band brake on the outermost periphery side.

  The invention according to claim 8 is the invention according to any one of claims 1 to 7, wherein the first one-way clutch, the second one-way clutch, and the first brake are arranged on an outer peripheral side within an axial dimension of the simple planetary gear mechanism. The third one-way clutch is arranged on the outer peripheral side within the axial dimension range of the Ravigneaux type planetary gear mechanism, and the piston of the first brake is arranged on the outer peripheral side of the band brake.

  The invention according to claim 1 provides a third connecting member in parallel with a second connecting member that integrally connects the carrier of the simple planetary gear mechanism and the second sun gear of the Ravigneaux type planetary gear mechanism, By configuring the carrier of the simple planetary gear mechanism and the second sun gear of the Ravigneaux type planetary gear mechanism integrally with the second clutch and the first one-way clutch, the automatic transmission and the hydraulic control device An increase in the axial dimension can be suppressed, and a shift shock associated with clutch engagement at the time of downshift at a specific shift stage can be reduced without adding a control sequence, so that the shift quality is also improved.

  The invention according to claim 2 is provided with a first clutch for connecting the carrier of the simple planetary gear mechanism and the first sun gear of the Ravigneaux type planetary gear mechanism, and the first connecting member includes the first clutch and the second one-way. By constituting the clutch, it is possible to reduce a shift shock at the time of upshift using the first clutch and the second one-way clutch.

  In the invention according to claim 3, by connecting the second one-way clutch to the fixing member by the first brake, the action of the second one-way clutch can be released / maintained by releasing / fastening the first brake. .

  The invention according to claim 4 is provided with a fourth connecting member that integrally connects the carrier and the fixing member of the Ravigneaux type planetary gear mechanism, and the fourth connecting member is constituted by a second brake and a third one-way clutch, The simple planetary gear mechanism and the Ravigneaux type planetary gear mechanism are arranged adjacent to each other, and the first one-way clutch, the second one-way clutch, and the third one-way clutch are arranged on the outer peripheral side within the axial dimensions of the simple planetary gear mechanism and the Ravigneaux type planetary gear mechanism. By arranging, the axial dimension of the automatic transmission can be further shortened.

  According to a fifth aspect of the present invention, the first one-way clutch and the second one-way clutch are arranged on the outer peripheral side within the axial dimension of the simple planetary gear mechanism, and the third one-way clutch is disposed within the axial dimension of the Ravigneaux type planetary gear mechanism. The axial dimension of the automatic transmission can be further shortened by being arranged on the outer peripheral side of the automatic transmission.

  The invention according to claim 6 has a fourth clutch that integrally connects the carrier and the input part of the Ravigneaux type planetary gear mechanism, and the first one-way clutch and the second one-way clutch are the same as the simple planetary gear mechanism. The third one-way clutch is disposed on the outer peripheral side within the axial dimension of the Ravigneaux type planetary gear mechanism, and the simple planetary gear mechanism and the Ravigneaux type planetary gear mechanism are disposed on one side adjacent to each other. By arranging 4 clutches and arranging the 1st clutch, 2nd clutch and 3rd clutch on the other side, the power transmission path can be easily routed, the structure can be simplified, and the automatic transmission itself Weight and inertia in the automatic transmission are also reduced.

  The invention according to claim 7 has a fourth clutch for integrally connecting the carrier and the input part of the Ravigneaux type planetary gear mechanism, and the first one-way clutch and the second one-way clutch are shafts of the simple planetary gear mechanism. The third one-way clutch is disposed on the outer peripheral side within the axial dimension of the Ravigneaux type planetary gear mechanism, and the simple planetary gear mechanism and the Ravigneaux type planetary gear mechanism are connected to the fourth one on the one side where they are connected. The clutch and output section are arranged, the first clutch, the second clutch, the third clutch and the band brake are arranged on the other side, and the third clutch, the second clutch and the first clutch are arranged from the inner peripheral side of the automatic transmission. The clutch plates of the first clutch, the second clutch, and the third clutch constituting the first clutch, the second clutch, and the third clutch overlap in the axial range. In addition, by arranging the band brake on the outermost periphery side, the axial dimension of the automatic transmission can be further shortened, and the clutch hydraulic circuit can be consolidated, so the circuit provided in the case etc. Simplified and good circuit handling.

  According to an eighth aspect of the present invention, the first one-way clutch, the second one-way clutch, and the first brake are arranged on the outer peripheral side within the axial dimension of the simple planetary gear mechanism, and the third one-way clutch is the Ravigneaux type planetary gear mechanism. Since the first brake piston is arranged on the outer peripheral side of the axial dimension range and on the outer periphery side of the band brake, the band brake actuator can be arranged through the first brake piston. The layout in the transmission can be simplified.

  Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.

  FIG. 1 shows the power for an FF vehicle (front engine front wheel drive vehicle) that employs an automatic transmission according to an embodiment of the present invention having three one-way clutches effective as a countermeasure for reducing a shift shock. FIG. 2 is an enlarged sectional view showing a region X which is the automatic transmission portion of FIG.

The power train shown in FIG. 1 has three axes of an input axis O ₁ , an idler axis O ₂ , and an output axis O ₃ arranged in parallel, and power from an engine (not shown) is placed on the input axis O _1. An input lockup torque converter 10, an oil pump P drivingly coupled to the pump impeller 11 of the torque converter 10, and a turbine runner 12 of the torque converter 10 and an input shaft (input unit) 1 are drivingly coupled. A planetary gear mechanism 20, a first drum clutch (first clutch) 30 that is drivingly coupled to the planetary gear mechanism 20, and a second drum clutch (second clutch) 40 that engages with the first drum clutch 30. , A third drum clutch (third clutch) 50 engaged with the second drum clutch 40, and the first drum clutch 3 A Ravigneaux type planetary gear mechanism 60 that is drivingly coupled to the zero and second drum clutches 40 and an output gear G1 that is drivingly coupled to the Ravigneaux type planetary gear mechanism 60 are arranged. On the idler axis O ₂ , an output gear ( The first idler gear G2 meshing with the output portion G1 and the second idler gear G3 meshing with the differential gear D are arranged, and the power from the output gear G1 extends from the differential gear D onto the output axis O _3. The power is transmitted so as to give a rotation difference to the two output shafts 2a and 2b.

  1 will be described in detail. The planetary gear mechanism 20 includes a so-called sun gear fixed type simple planetary gear mechanism in which a sun gear 20s is fixed to a transmission case 100 via an intermediate member M as shown in FIG. The ring gear 20r is integrally attached to the input shaft 1, and is composed of a sun gear 20s and a carrier 20c that is drive-coupled via a pinion gear 20p that meshes with the ring gear 20r. The carrier 20c is a first drum. The clutch 30 is connected to the first clutch hub 31. For this reason, the input rotation from the input shaft 1 transmitted from the ring gear 20r is transmitted to the first drum clutch 30 via the carrier 20c.

  The first drum clutch 30 is a 3-5 speed reverse clutch, and includes a first clutch hub 31 provided with a plurality of clutch plates (clutch plates of the first clutch) 33 on the outer periphery, and the first clutch hub 31 A first clutch drum 32 having a plurality of clutch plates (clutch plates of the first clutch) 34 arranged alternately with a clearance from the clutch plate 33 on the inner periphery, and an inner side of the first clutch drum 32 It comprises a hydraulic first clutch piston 35 supported by a spring S1 in the cylinder chamber with a peripheral portion as a cylinder chamber.

  For this reason, when hydraulic pressure acts on the first clutch piston 35, the first drum clutch 30 presses the clutch plates 33, 34 against the spring force to press the clutch plates 33, 34. The first clutch hub 31 and the first clutch drum 32 are brought into a state in which the first clutch hub 31 and the first clutch drum 32 can rotate integrally, and when the hydraulic pressure applied to the first clutch piston 35 is released, the first clutch piston 35 becomes spring force. Thus, the first clutch hub 31 and the first clutch drum 32 can be rotated relative to each other by releasing the space between the clutch plates 33 and 34 away from the clutch plates 33 and 34.

The first clutch drum 32 is drivingly coupled to the first sun gear 60s ₁ of the Ravigneaux type planetary gear mechanism 60, and a brake constituting a band brake B for inducing braking on the transmission case (fixed member) 100 on the outer periphery thereof. The band Bo is exteriorized.

  For this reason, when the brake band Bo is wound around the first clutch drum 32, the band brake B presses the first clutch drum 32 to cause friction between the brake band Bo and the first clutch drum 32. The first clutch drum 32 is brought into a state in which the first clutch drum 32 can be stopped or decelerated with respect to the transmission case 100, and when the winding of the brake band Bo is released, the brake band Bo is separated from the first clutch drum 32. By releasing the space between the brake band Bo and the first clutch drum 32, the first clutch drum 32 can be rotated.

  On the other hand, the first clutch hub 31 has a second drum clutch 40 that itself functions as a clutch drum. The second drum clutch 40 is a low clutch, and includes a first clutch hub (second clutch drum) 31 provided with a plurality of clutch plates (second clutch clutch plates) 43 on the inner periphery, and the clutch plates 43. And a second clutch hub 42 having a plurality of clutch plates (clutch plates of the second clutch) 44 arranged alternately with a gap therebetween, and an inner peripheral portion of the first clutch hub 31 as a cylinder chamber The hydraulic second clutch piston 45 is housed in the cylinder chamber.

The second drum clutch 40 attaches the outer race C1a of the first one-way clutch C1, which is a forward one-way clutch, to the second clutch hub 42, while the Ravigneaux type planetary gear mechanism is attached to the inner race C1b of the first one-way clutch C1. By attaching 60 second sun gears 60s ₂ , the second sun gear 60s ₂ is drivingly coupled via the first one-way clutch C1.

For this reason, when hydraulic pressure acts on the second clutch piston 45, the second drum clutch 40 presses the clutch plates 43, 44 to engage the clutch plates 43, 44 with frictional force. When the first clutch hub 31 and the second sun gear 60s ₂ are integrally rotatable only in one direction by the first one-way clutch C1, the clutch plates 43 and 44 are released when the hydraulic pressure applied to the second clutch piston 45 is released. The first clutch hub 31 and the second sun gear 60s ₂ are brought into a state in which they can be rotated relative to each other by releasing the clearance between the clutch plates 43 and 44.

The second clutch piston 45 also has a third drum clutch 50 that itself functions as a clutch drum. That is, the third drum clutch 50 is also a coasting clutch, and a hydraulic second clutch piston (third clutch drum) 45 having a plurality of clutch plates (clutch plates of the third clutch) 53 on the outer periphery, A third clutch hub 52 that is provided with a plurality of clutch plates (clutch plates of a third clutch) 54 that are alternately arranged with a clearance from these clutch plates 53 on the outer periphery, and that is drivingly coupled to the second sun gear 60s ₂ ; and a third clutch piston 55. inner peripheral portion of the hydraulic supported by a spring S ₂ to the cylinder chamber as a cylinder chamber of the second clutch piston 45.

For this reason, when hydraulic pressure acts on the third clutch piston 55, the third drum clutch 50 presses the clutch plates 53, 54 to engage the clutch plates 53, 54 with frictional force. while the second clutch piston 45 to the ready to rotate the second sun gear 60s ₂ integrally Te, to release the hydraulic pressure acting on the third clutch piston 55, the third clutch piston 55 the clutch plate 53, The second clutch piston 45 and the second sun gear 60 s ₂ are brought into a state in which the second clutch piston 45 and the second sun gear 60 s ₂ can be rotated relative to each other by releasing the gap between the clutch plates 53 and 54.

Ravigneaux type planetary gear mechanism 60, as shown in FIG. 2, the driven coupling via the first sun gear 60s ₁ and the second clutch hub 42 which is drivingly connected to the first clutch drum 32 first one-way clutch C1 a second sun gear 60s _2, a second pinion 60p ₂ (shown in FIG. 2, two-dot chain line) of the first pinion 60p ₁ and the second sun gear 60s ₂ mesh to the first sun gear 60s ₁ and meshing the first pinion 60p ₁ and a carrier 60c that the second pinion 40p ₂ rotatably supported, and a first pinion 60p ₁ and meshes with a ring gear 60r which is drivingly connected to the output gear G1.

In particular, the first sun gear 60 s ₁ is connected to the band brake B via the first clutch drum 32, and the inner race C 2 b of the second one-way clutch C 2 that is a second one-way clutch is attached to the first clutch drum 32. On the other hand, by attaching a multi-plate brake 70 as a first brake for inducing braking to the transmission case 100 to the outer race C2a of the second one-way clutch C2, the second one-way clutch C2 is attached to the first brake 70. Connected through.

The first brake 70 is a two-speed brake, and a plurality of clutch plates 73 provided in the outer race C2a of the second one-way clutch C2 and the clutch plates 73 are alternately arranged with a gap therebetween to change the speed. A plurality of clutch plates 74 provided in the machine case 100 and a hydraulic first brake piston (piston of the first brake 70) supported by a spring (not shown) along the input axis O ₁ (idler axis or output axis) ) 75. As shown in FIG. 2, the first brake piston 75 includes two members 75 a and 75 b that extend along the input shaft 1 and can be attached and detached. The member 75 a is formed in the transmission case 100. The pressure receiving part is disposed in the cylinder 100r and has a pressure receiving surface that receives the hydraulic pressure supplied into the cylinder 100r, and the other member 75b is a pressing part that contacts the clutch plates 73 and 74. The pressing part 75a and the pressure receiving part 75b may be simply brought into contact with each other, or may be fitted and detachably fitted.

For this reason, when hydraulic pressure acts on the first brake piston 75, the first multi-plate brake 70 presses the clutch plates 73, 74 and the clutch plates 73, 74 are fastened by frictional force. while the first sun gear 60s ₁ and the first clutch drum 32 in a state that can only rotate in one direction relative to the transmission case 100, to release the hydraulic pressure acting on the first brake piston 75, the first 1 the brake piston 75 is ready to rotate the first sun gear 60s ₁ and the first clutch drum 32 by releasing between clutch plates 73 and 74 away from the clutch plates 73, 74.

  Similarly, the carrier 60c is attached to the transmission case 100 via a second brake 80 and a third one-way clutch C3 that cause braking to the transmission case 100.

  The second brakes 80 are low-and-reverse brakes, and are arranged alternately with hubs 81 having a plurality of clutch plates 83 provided on the outer periphery of the carrier 60c, with these clutch plates 83 spaced from each other. The multi-plate brake includes a plurality of clutch plates 84 provided in the transmission case 100 and a hydraulic second brake piston 85 housed in a cylinder chamber provided in the transmission case 100. The third one-way clutch C3 is a low one-way clutch, and the inner race C3b is attached to the carrier 60c, while the transmission case 100 is attached to the outer race C3a, and the carrier 60c is attached to the transmission case 100. 3 one-way clutch C3.

  For this reason, when hydraulic pressure is applied to the second brake piston 85, the second brake 80 presses the clutch plates 83, 84 to engage the clutch plates 83, 84 with frictional force. When the carrier 60c is fixed to the transmission case 100 and the hydraulic pressure applied to the second brake piston 85 is released, the second brake piston 85 moves away from the clutch plates 83 and 84 and moves between the clutch plates 83 and 84. By releasing the carrier 60c, the third one-way clutch C3 allows the transmission case 100 to rotate only in one direction.

  The ring gear 60 r is connected to the output gear G 1 and is drivingly coupled to the input shaft 1 via a fourth drum clutch (fourth clutch) 90. The fourth drum clutch 90 is a high clutch, and includes a plurality of clutch plates 93 provided on the outer periphery of the carrier 60c, and a plurality of clutch plates 94 arranged alternately with these clutch plates 93 spaced apart from each other. A clutch drum 92 provided on the input shaft 1 and a hydraulic fourth clutch piston 95 supported by a spring S3 in the cylinder chamber with the inner peripheral portion of the clutch drum 92 as a cylinder chamber.

  For this reason, when hydraulic pressure acts on the fourth clutch piston 95, the fourth drum clutch 90 presses the clutch plates 93, 94 to engage the clutch plates 93, 94 with frictional force. Thus, when the carrier 60c can be rotated integrally with the input shaft 1 and the hydraulic pressure applied to the fourth clutch piston 95 is released, the fourth clutch piston 95 moves away from the clutch plates 93, 94, and the clutch plate 93 , 94 is released so that the carrier 60c can rotate relative to the input shaft 1.

  That is, the Ravigneaux type planetary gear mechanism 60 of the present embodiment is a ring gear output transmission mechanism that is a sun gear fixed carrier input or a carrier fixed sun gear input by fastening and releasing by the band brake B and the multi-plate brakes 70, 80, 90. .

As is apparent from the configuration on the input axis O _{1 in} FIGS. 1 and 2, in the present embodiment, the carrier 20 c of the simple planetary gear mechanism 20 and the second sun gear 60 S ₂ of the Ravigneaux type planetary gear mechanism 60 are integrally connected. the third connecting member provided in parallel with the coupling member, said third coupling member, the simple planetary gear mechanism 20 two sets of clutch the second sun gear 60S ₂ of the carrier 20c and the Ravigneaux type planetary gear mechanism 60 integrally connecting the first By comprising the two-drum clutch 40 and the first one-way clutch C1, it is possible to suppress the increase in the axial dimension of the automatic transmission and the hydraulic control device, and at a specific shift stage without adding a control sequence. When shifting down, specifically, the shift shock associated with clutch engagement at the time of 5 to 4 shifts can be reduced. Quality is also improved.

  Further, in the present embodiment, a first drum clutch 30 that connects the carrier 20c of the simple planetary gear mechanism 20 and the first sun gear 60S1 of the Ravigneaux type planetary gear mechanism 60 is provided, and the first connecting member is the first drum clutch 30. By constituting the second one-way clutch C2, it is possible to reduce the shift shock at the time of upshift using the first drum clutch 30 and the second one-way clutch C2.

  In the present embodiment, a fourth connecting member for integrally connecting the carrier 60c of the Ravigneaux type planetary gear mechanism 60 and the transmission case 100 is provided, and the fourth connecting member is constituted by the second brake 80 and the third one-way clutch C3. By doing so, the reaction force of the carrier 60c can be received by the transmission case 100 at the time of 1 → 2 speed upshift acceleration and 2 → 1 speed downshift.

  In this embodiment, the simple planetary gear mechanism 20 and the Ravigneaux type planetary gear mechanism 60 are arranged adjacent to each other, and the first one-way clutch C1, the second one-way clutch C2, and the third one-way clutch C3 are the simple planetary gear mechanism 20 and the Ravigneaux type planetary gear mechanism. By disposing on the outer peripheral side within the axial dimension of 60, the axial dimension of the automatic transmission can be further shortened.

  In the present embodiment, the first one-way clutch C1 and the second one-way clutch C2 are arranged on the outer peripheral side within the axial dimension of the simple planetary gear mechanism 20, and the third one-way clutch C3 is within the axial dimension of the Ravigneaux type planetary gear mechanism 60. The axial dimension of the automatic transmission can be further shortened by being arranged on the outer peripheral side of the automatic transmission.

  This embodiment has a fourth clutch that integrally connects the carrier 60c of the Ravigneaux type planetary gear mechanism 60 and the input shaft 1, and the first one-way clutch C1 and the second one-way clutch C2 are shafts of the simple planetary gear mechanism 20. The third one-way clutch C3 is disposed on the outer peripheral side within the axial dimension of the Ravigneaux type planetary gear mechanism 60, and the simple planetary gear mechanism 20 and the Ravigneaux type planetary gear mechanism 60 are disposed on one side adjacent to each other. Since the fourth drum clutch 90 is arranged and the first drum clutch 30, the second drum clutch 40, and the third drum clutch 50 are arranged on the other side, the power transmission path is easily routed and the structure is simplified. The weight of the automatic transmission itself and the inertia in the automatic transmission are also reduced.

The present embodiment includes a fourth drum clutch 90 that integrally connects the carrier 60c of the Ravigneaux type planetary gear mechanism 60 and the input shaft 1, and the first one-way clutch C ₁ and the second one-way clutch C2 are simple planetary gear mechanisms. The third one-way clutch C3 is arranged on the outer peripheral side within the axial dimension of the Ravigneaux type planetary gear mechanism 60, and the simple planetary gear mechanism 20 and the Ravigneaux type planetary gear mechanism 60 are arranged contiguously. A fourth drum clutch 90 and an output gear (output unit) G1 are arranged on one side, and a first drum clutch 30, a second drum clutch 40, a third drum clutch 50 and a band brake B are arranged on the other side, and automatic A third drum clutch 50, a second drum clutch 40, and a first drum clutch 30 are arranged from the inner peripheral side of the transmission, and are axially The clutch plates 33 and 34 of the first clutch, the clutch plates 43 and 44 of the second clutch, and the clutch plate 53 of the third clutch constituting the first drum clutch 30, the second drum clutch 40, and the third drum clutch 50. , 54 are arranged so that they overlap, and in addition, the band brake B is arranged on the outermost peripheral side, so that the axial dimension of the automatic transmission can be further shortened and can be integrated into the clutch hydraulic circuit. The circuit provided in the circuit is simplified and the circuit can be easily handled.

  In this embodiment, the first one-way clutch C1, the second one-way clutch C2, and the first brake 70 are arranged on the outer peripheral side in the axial dimension of the simple planetary gear mechanism 20, and the third one-way clutch C3 is the Ravigneaux type planetary gear mechanism 60. By disposing the first brake piston 75 of the first brake 70 on the outer peripheral side of the axial dimension range and on the outer peripheral side of the band brake B, the actuator of the band brake B can be disposed through the piston 75. The layout in the self-propelled transmission can be simplified.

3 to 9 are skeleton diagrams showing the automatic transmission (excluding the torque converter) arranged on the input axis O ₁ of the present embodiment, and FIGS. 3 to 8 are from the first speed to the sixth speed, respectively. FIG. 9 shows a power transmission path during reverse (reverse). However, the path through which power is actually transmitted is indicated by a thick line, and the path through which power is actually transmitted is indicated by a thin line.

In these cases, in any power transmission from the first speed to the sixth speed, the first one-way clutch C1 includes the carrier 20c of the simple planetary gear mechanism 20 as the second connecting member and the Ravigneaux type planetary gear mechanism 60 in the forward range. Forward rotation in the same direction as the engine rotation in the second sun gear 60S ₂ is disabled, the reverse rotation is enabled, the second drum clutch 40 is engaged when the forward range is accelerated in the engaged state, and the second one-way clutch C2 is When downshifting from the third speed to the second speed, the first brake 70 is engaged in a direction to prevent reverse rotation of the first connecting member in the engaged state, and the third one-way clutch C3 is the third connecting member at the first speed. The forward rotation that rotates in the same direction as the engine rotation in the carrier 60c of the Ravigneaux type planetary gear mechanism 60 is enabled, and the reverse rotation is disabled.

It is sectional drawing which shows the power train for FF vehicles which employ | adopted the automatic transmission which is one Embodiment of this invention provided with the one-way clutch. It is an expanded sectional view which shows the area | region X of FIG. FIG. 2 is a skeleton diagram showing a power transmission path at the first speed in the automatic transmission arranged on the input axis line of FIG. 1. FIG. 3 is a skeleton diagram showing a power transmission path at a second speed in the automatic transmission arranged on the input axis line of FIG. 1. FIG. 4 is a skeleton diagram showing a power transmission path at a third speed in the automatic transmission arranged on the input axis line of FIG. 1. FIG. 6 is a skeleton diagram showing a power transmission path at a fourth speed in the automatic transmission arranged on the input axis in FIG. 1. FIG. 6 is a skeleton diagram showing a power transmission path at the fifth speed in the automatic transmission arranged on the input axis line of FIG. 1. FIG. 6 is a skeleton diagram showing a power transmission path at a sixth speed in the automatic transmission arranged on the input axis line of FIG. 1. FIG. 2 is a skeleton diagram showing a power transmission path during reverse in the automatic transmission arranged on the input axis line of FIG. 1. It is a schematic cross section which illustrates the conventional automatic transmission provided with the one-way clutch.

Explanation of symbols

1 Input shaft 2 Output shaft
10 Lock-up torque converter
20 Simple planetary gear mechanism
20s sun gear
20c career
20r ring gear
30 1st drum clutch
31 1st clutch hub
32 1st clutch drum
35 1st clutch piston (2nd clutch drum)
40 Second drum clutch
42 Second clutch hub
45 Second clutch piston (third clutch drum)
50 3rd drum clutch
52 3rd clutch hub
55 3rd clutch piston
60 Ravigneaux planetary gear mechanism
60s ₁ first sun gear
60s ₂ second sun gear
60c career
60r ring gear
70 First brake
80 Second brake
90 4th drum clutch B Band brake Bo Brake band C1 1st one way clutch C2 2nd one way clutch C3 3rd one way clutch

Claims (8)

An input unit that inputs rotation from the drive source, an output unit that outputs the rotated rotation, a plurality of connecting members that integrally connect the plurality of rotating elements, an input unit, an output unit, a connecting member, and two It is arranged between the rotating elements of the planetary gears of the set and includes four clutches that are selectively connected and disconnected and three brakes that are selectively fixed, and by appropriately engaging and releasing the four clutches and the three brakes. , A gear transmission for an automatic transmission having shift control means for obtaining at least 6 forward speeds and 1 reverse speed,
The two sets of planetary gears are composed of a simple planetary gear mechanism and a Ravigneaux type planetary gear mechanism,
The simple planetary gear mechanism is a reduction device that constantly decelerates the input rotation of the input unit, and the Ravigneaux type planetary gear mechanism includes two sets of sun gears, a first sun gear and a second sun gear, and a short pinion that meshes with the first sun gear. And a long pinion that meshes with the second sun gear, a carrier that integrally supports the short pinion and the long pinion, and a ring gear that meshes with the short pinion, the Ravigneaux type planetary gear mechanism, A first clutch having a first connecting member for integrally connecting the first sun gear of the Ravigneaux type planetary gear mechanism, a first clutch for integrally connecting the carrier of the simple planetary gear mechanism and the second sun gear of the Ravigneaux type planetary gear mechanism. An automatic transmission having a third clutch having two connecting members;
A third connection member is provided in parallel with the second connection member, and the third connection member is a second set of clutches that integrally connect the carrier of the simple planetary gear mechanism and the second sun gear of the Ravigneaux type planetary gear mechanism. An automatic transmission comprising two clutches and a first one-way clutch. Providing a first clutch for connecting the carrier of the simple planetary gear mechanism and the first sun gear of the Ravigneaux type planetary gear mechanism;
The automatic transmission according to claim 1, wherein the first connecting member includes the first clutch and a second one-way clutch.   The automatic transmission according to claim 2, wherein the second one-way clutch is connected to a fixed member by a first brake. A fourth connecting member for integrally connecting the carrier and the fixing member of the Ravigneaux type planetary gear mechanism is provided, and the fourth connecting member is constituted by a second brake and a third one-way clutch;
The simple planetary gear mechanism and the Ravigneaux type planetary gear mechanism are arranged adjacent to each other, and the first one-way clutch, the second one-way clutch, and the third one-way clutch are arranged on the outer peripheral side within the axial dimensions of the simple planetary gear mechanism and the Ravigneaux type planetary gear mechanism. The automatic transmission according to any one of claims 1 to 3, wherein the automatic transmission is arranged.   The first one-way clutch and the second one-way clutch are disposed on the outer peripheral side within the axial dimension of the simple planetary gear mechanism, and the third one-way clutch is disposed on the outer peripheral side within the axial dimension of the Ravigneaux type planetary gear mechanism. 5. The automatic transmission according to claim 4, wherein A fourth clutch for integrally connecting the carrier and the input part of the Ravigneaux type planetary gear mechanism;
The first one-way clutch and the second one-way clutch are arranged on the outer peripheral side within the axial dimension of the simple planetary gear mechanism, and the third one-way clutch is arranged on the outer peripheral side within the axial dimension of the Ravigneaux type planetary gear mechanism,
2. The simple planetary gear mechanism and the Ravigneaux type planetary gear mechanism are characterized in that the fourth clutch is disposed on one side adjacent to each other, and the first clutch, the second clutch, and the third clutch are disposed on the other side. The automatic transmission as described in any one of thru | or 5. A fourth clutch for integrally connecting the carrier and the input part of the Ravigneaux type planetary gear mechanism;
The first one-way clutch and the second one-way clutch are arranged on the outer peripheral side within the axial dimension of the simple planetary gear mechanism, and the third one-way clutch is arranged on the outer peripheral side within the axial dimension of the Ravigneaux type planetary gear mechanism,
The simple planetary gear mechanism and the Ravigneaux type planetary gear mechanism are arranged such that the fourth clutch and the output part are arranged on one side of the connected arrangement, and the first clutch, the second clutch, the third clutch and the band brake are arranged on the other side,
The third clutch, the second clutch, and the first clutch are arranged from the inner peripheral side of the automatic transmission, and the first clutch, the second clutch, and the second clutch that configure the first clutch, the second clutch, and the third clutch in the axial range. The automatic transmission according to any one of claims 1 to 6, wherein the clutch plates of the three clutches are arranged so as to overlap with each other, and in addition, a band brake is arranged on the outermost peripheral side. The first one-way clutch, the second one-way clutch and the first brake are arranged on the outer peripheral side within the axial dimension of the simple planetary gear mechanism,
The third one-way clutch is disposed on the outer peripheral side within the axial dimension range of the Ravigneaux type planetary gear mechanism,
The automatic transmission according to any one of claims 1 to 7, wherein a piston of the first brake is disposed on an outer peripheral side of the band brake.

Images