JP2006161927A - Variable speed gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To increase the number of variable speed gear stages and prevent the number of parts and the dimension and weight of a variable speed gear from increasing. <P>SOLUTION: The variable speed gear is provided with first to fifth rotation elements from one end to the other end in a first variable speed gear part comprised of a differential rotation, and a velocity diagram. The variable speed gear has a second variable speed gear part comprised of a plurality of differential rotation devices, and changes gear in at least seven change gear stages of eight change gear stages by making input and output states of rotations for each rotation element of the second change gear part. In this case, when there are present a frictional engagement element engaged at the first to fifth speeds, a frictional engagement element engaged at the fifth to eighth speeds, a frictional engagement element at the second and eighth speeds, a frictional engagement element at the third and seventh speeds, a frictional engagement element at the fourth and sixth speeds, and a frictional engagement element at the first speed, the first to eighth speeds can be achieved. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a transmission.

2. Description of the Related Art Conventionally, a transmission, for example, an automatic transmission, has a transmission including a plurality of planetary gear units and a plurality of clutches, brakes, and the like. The transmission path is changed, and the gear ratio is changed accordingly, so that a plurality of shift stages are achieved. For this purpose, each planetary gear unit includes a sun gear, a ring gear, a pinion that meshes with the sun gear and the ring gear, and a carrier that supports the pinion. The input / output of rotation with respect to the planetary gear unit is switched, and, for example, a 1st to 7th gear is achieved during forward travel (see, for example, Patent Document 1).
JP 2000-266138 A

  However, in the conventional transmission, in order to increase the number of shift stages to be achieved, it is necessary to increase the number of planetary gear units or the number of clutches, brakes, etc., and the number of parts is increased. Not only will it increase, but the size and weight of the transmission will increase and the cost will increase.

  The present invention solves the problems of the conventional transmission and can increase the number of shift stages achieved, and does not increase the number of parts or increase the size and weight. An object is to provide a transmission.

  For this purpose, in the transmission of the present invention, a first rotary rotation device including a rotation element to which the rotation of the input member is input, a rotation element fixed to the non-rotation member, and a rotation element to which the rotation is output is provided. 1 has a second transmission unit that includes a plurality of differential rotation devices and includes first to fifth rotation elements from one end to the other end. By changing the input / output state of rotation for each rotary element of the first and second transmission units, shifting is performed at at least seven of the eight shift stages.

  Then, the rotation of each gear stage is output to the output member from the fourth rotating element, and the rotation of the input member is input to the fifth rotating element at the first speed, and the third rotating element is connected to the non-rotating member. In the second speed, the rotation of the input member is input to the fifth rotating element, the second rotating element is connected to the non-rotating member, and in the third speed, the input member rotates to the fifth rotating element. The rotation of the first transmission unit is input to the second rotation element, the rotation of the input member is input to the fifth rotation element at the fourth speed, and the first rotation element is the non-rotation member. In the fifth speed, the rotation of the input member is input to the third and fifth rotating elements at the fifth speed, and the rotation of the input member is input to the third rotating element at the sixth speed. It is connected to a non-rotating member and enters the third rotating element at the seventh speed. The rotation of the member is input, the rotation of the first transmission unit is input to the second rotation element, the rotation of the input member is input to the third rotation element at the eighth speed, and the second rotation element It is connected with a non-rotating member.

  In another transmission of the present invention, the rotation of the first transmission unit is further output as a predetermined friction engagement element is engaged.

  In still another transmission according to the present invention, the friction engagement element is disposed between the first and second transmission units.

  In still another transmission according to the present invention, the friction engagement element is disposed between the first transmission unit and the input member.

  In still another transmission according to the present invention, the friction engagement element is disposed between the first transmission unit and the non-rotating member.

  In still another transmission according to the present invention, the second transmission unit further includes first and second differential rotation devices. The first to fifth rotating elements include a sun gear of the first differential rotating device, a sun gear of the second differential rotating device, a ring gear of the first differential rotating device, and a second differential rotating device. This is a carrier common to the ring gear and the first and second differential rotating devices.

  In still another transmission according to the present invention, the second transmission unit further includes first and second differential rotation devices. The first to fifth rotating elements include a sun gear of the second differential rotating device, a carrier common to the first and second differential rotating devices, a ring gear of the first differential rotating device, and a second gear. These are the ring gear of the differential rotation device and the sun gear of the first differential rotation device.

  In still another transmission according to the present invention, the first clutch to the third clutch disposed between the rotating elements, and the first brake disposed between the rotating element and the non-rotating member. A third brake is provided. The first clutch is engaged at 1st to 5th speed, the second clutch is engaged at 5th to 8th speed, the third clutch is engaged at 3rd and 7th speed, The first brake is engaged at the second speed and the eighth speed, the second brake is engaged at the fourth speed and the sixth speed, and the third brake is engaged at the first speed.

  In still another transmission according to the present invention, the first clutch and the second clutch disposed between the rotating elements, and the first brake disposed between the rotating element and the non-rotating member. A fourth brake is provided. The first clutch is engaged at 1st to 5th speed, the second clutch is engaged at 5th to 8th speed, the first brake is engaged at 2nd and 8th speed, The second brake is engaged at the fourth speed and the sixth speed, the third brake is engaged at the first speed, and the fourth brake is engaged at the third speed and the seventh speed.

  According to the present invention, the transmission includes a rotating element that receives the rotation of the input member, a rotating element that is fixed to the non-rotating member, and a differential rotating apparatus that includes the rotating element that outputs the rotation. 1 has a second transmission unit that includes a plurality of differential rotation devices and includes first to fifth rotation elements from one end to the other end. By changing the input / output state of rotation for each rotary element of the first and second transmission units, shifting is performed at at least seven of the eight shift stages.

  Then, the rotation of each gear stage is output to the output member from the fourth rotating element, and the rotation of the input member is input to the fifth rotating element at the first speed, and the third rotating element is connected to the non-rotating member. In the second speed, the rotation of the input member is input to the fifth rotating element, the second rotating element is connected to the non-rotating member, and in the third speed, the input member rotates to the fifth rotating element. The rotation of the first transmission unit is input to the second rotation element, the rotation of the input member is input to the fifth rotation element at the fourth speed, and the first rotation element is the non-rotation member. In the fifth speed, the rotation of the input member is input to the third and fifth rotating elements at the fifth speed, and the rotation of the input member is input to the third rotating element at the sixth speed. It is connected to a non-rotating member and enters the third rotating element at the seventh speed. The rotation of the member is input, the rotation of the first transmission unit is input to the second rotation element, the rotation of the input member is input to the third rotation element at the eighth speed, and the second rotation element It is connected with a non-rotating member.

  In this case, friction engagement elements that are engaged at the 1st to 5th speeds, friction engagement elements that are engaged at the 5th to 8th speeds, friction engagement elements that are engaged at the 2nd and 8th speeds, and 3rd speed 1st to 8th speeds are achieved if there is a friction engagement element that is engaged at the 7th speed and a friction engagement element that is engaged at the 4th and 6th speeds and a friction engagement element that is engaged at the 1st speed. Therefore, the number of shift speeds achieved can be increased, and the number of parts is not increased, and the size and weight are not increased.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In this case, a transmission device for an automatic transmission as a transmission will be described.

  FIG. 1 is a schematic diagram of the transmission according to the first embodiment of the present invention, FIG. 2 is a diagram showing an operation table of the transmission according to the first embodiment of the present invention, and FIG. 3 is the first diagram of the present invention. It is a speed diagram of the transmission in an embodiment.

  In the figure, 10 is a transmission case as a casing and a non-rotating member, 11 is a transmission accommodated in the transmission case 10, and the transmission 11 is similarly changed in speed. An automatic transmission is configured together with a torque converter (not shown) as a fluid transmission device housed in the machine case 10. The torque converter is connected to a crankshaft of an engine (not shown), receives rotation generated by the engine, and transmits it to an input shaft 20 as an input member of the transmission 11 through oil as a working fluid. When the vehicle speed exceeds the set value, a lockup clutch (not shown) is engaged, and the rotation generated by the engine is directly transmitted to the input shaft 20. In the transmission 11, the side where the torque converter is disposed (the right side in FIG. 1) is the front, and the opposite side (the left side in FIG. 1) is the rear.

  The transmission 11 is a transmission for an FF vehicle that performs a shift of eight forward speeds and one reverse speed, a double pinion type planetary gear unit PF as a first transmission unit and a differential rotation device, A gear train comprising a combination with a Ravigneaux type planetary gear unit PR serving as a second transmission unit is provided. The planetary gear unit PR includes first and second double pinion type first and second differential rotation devices. 2 planetary gear units G1 and G2. The gear ratios of the planetary gear unit PF and the first and second planetary gear units G1 and G2 are λ1 to λ3. In the present embodiment, the transmission 11 is configured by the planetary gear units PF and PR, but can also be configured by three or more planetary gear units.

  The planetary gear unit PF includes a sun gear S1 as a first differential rotation element, a ring gear R1 as a second differential rotation element, a pinion P1a that meshes with the sun gear S1, a pinion P1b that meshes with the ring gear R1 and the pinion P1a. And a carrier CR1 as a third differential rotating element, and the pinions P1a and P1b are supported by the carrier CR1. The sun gear S1 is connected to the transmission case 10 and the carrier CR1 is connected to the transmission case 10 as an input element indicating a rotating element to which the rotation of the input shaft 20 is input, the ring gear R1 is an output element indicating a rotating element to which the rotation is output. And functions as a fixed element that represents a rotating element that generates a reaction force. The pinions P1a and P1b function as first and second transmission elements.

  The planetary gear unit PR includes a sun gear S2 as a first differential rotation element, a sun gear S3 as a second differential rotation element, a ring gear R2 as a third differential rotation element, and a fourth differential rotation element. Ring gear R3, pinion P2a meshing with the sun gear S2, pinion P2b meshing with the ring gear R2 and pinion P2a, pinion P3a meshing with the sun gear S3, pinion P3b meshing with the ring gear R3 and pinion P3a, and a fifth Carriers CR2 and CR3 are provided as differential rotating elements, and pinions P2a and P2b are supported by the carrier CR2, and pinions P3a and P3b are supported by a carrier CR3 formed integrally with the carrier CR2.

  The sun gears S2 and S3 function as fixed elements, the ring gear R2 functions as an input element or a fixed element, the ring gear R3 functions as an output element, and the carriers CR2 and CR3 function as input elements. The pinions P2a and P3a form an integral long pinion, and the pinions P2b and P3b form a short pinion. The pinions P2a and P3a function as a first transmission element, the pinion P2b functions as a second transmission element, and the pinion P3b functions as a third transmission element. The first planetary gear unit G1 includes a sun gear S2, a ring gear R2, pinions P2a and P2b, and a carrier CR2. The second planetary gear unit G2 includes a sun gear S3, a ring gear R3, pinions P3a and P3b, and a carrier CR3. The

  The power transmission path in the transmission 11 is changed by engaging / disengaging the clutches C1 to C3 and the brakes B1 to B3 as friction engagement elements and switching the input / output of rotation in the planetary gear units PF and PR. Accordingly, the gear ratio is changed, and a plurality of shift speeds of the eighth speed in the forward direction and the first speed in the reverse direction are achieved in the present embodiment. Note that it is also possible to achieve the seventh speed by not using any one of the eight speed gears during forward movement. In order to engage / disengage the clutches C1 to C3, brakes B1 to B3, etc., a hydraulic servo or the like (not shown) is provided as an engagement / disengagement device. The clutches C1 to C3 constitute a first clutch to a third clutch, and the brakes B1 to B3 constitute a first brake to a third brake.

  In the planetary gear unit PF, the sun gear S1 is connected to the input shaft 20, and the ring gear R1 is selectively connected to the sun gear S3 via the clutch C3 and to the transmission case 10 via the clutch C3 and the brake B1. The carrier CR1 is connected to the transmission case 10 and selectively connected to the sun gear S2 via the brake B2.

  In the planetary gear unit PR, the sun gear S2 is selectively connected to the carrier CR1 via the brake B2, and the ring gear R2 is connected to the input shaft 20 via the clutch C2 and to the transmission case via the brake B3. The sun gear S3 is selectively connected to the ring gear R1 via the clutch C3 and to the transmission case 10 via the brake B1, and the ring gear R3 is connected to the output shaft 12 as an output member. The carriers CR2 and CR3 are coupled to each other and selectively coupled to the input shaft 20 via the clutch C1 and to the ring gear R2 via the clutches C1 and C2.

  The output shaft 12 constitutes a counter drive shaft to which an output gear 50 is attached. The output gear 50 constitutes a counter drive gear and meshes with a counter driven gear attached to a counter driven shaft (not shown). The counter driven shaft is connected to driving wheels (not shown) via a differential device (not shown).

  In the present embodiment, in order to change the power transmission path in the transmission 11, the planetary gear unit PF includes three differential rotation elements, and the planetary gear unit PR includes five differential rotation elements. However, the planetary gear unit PF can include four or more differential rotation elements, and the planetary gear unit PR can include six or more differential rotation elements.

  By the way, as shown in the operation table of FIG. 2, the clutches C1 to C3 and the brakes B1 to B3 are disengaged, the parking range (P), the reverse range (R) as the reverse travel range, and the neutral range as Each range of a neutral range (N) and a drive range (D) as a forward travel range is set, and in the drive range, each gear stage from 1st to 8th is achieved at each gear ratio. In FIG. 2, ◯ represents engagement, and the others represent release. Further, the non-traveling range is configured by the parking range and the neutral range, and the traveling range is configured by the reverse range and the drive range.

  Next, the operation of the transmission 11 will be described according to the operation table.

  First, in the first speed of the drive range, the clutch C1 and the brake B3 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the carriers CR2 and CR3 via the clutch C1, and the rotation of the ring gear R2 is prevented with the engagement of the brake B3.

  Therefore, the rotation of the input shaft 20 input to the carriers CR2 and CR3 is decelerated by the fixed ring gear R2 while the sun gears S2 and S3 are idling in the reverse direction, and is output to the ring gear R3 and forwardly forward in the first speed. Is output to the output gear 50.

  In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, and output to the ring gear R1, but since the clutch C3 is released, the rotation to the sun gear S3 Is not transmitted.

  In the second speed of the drive range, the clutch C1 and the brake B1 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the carriers CR2 and CR3 via the clutch C1, and the rotation of the sun gear S3 is prevented with the engagement of the brake B1.

  As a result, the rotation of the input shaft 20 input to the carriers CR2 and CR3 is decelerated by the fixed sun gear S3, and is output to the ring gear R3, and the second-speed positive rotation that is faster than the first-speed rotation is output. It is output to the gear 50.

  In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, and output to the ring gear R1, but since the clutch C3 is released, the rotation to the sun gear S3 Is not transmitted.

  In the third speed of the drive range, the clutches C1 and C3 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the carriers CR2 and CR3 via the clutch C1. In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, output to the ring gear R1, and input to the sun gear S3 via the clutch C3. Therefore, the rotation of the input shaft 20 input to the carriers CR2 and CR3 is further decelerated by the rotation input to the sun gear S3, and is output to the ring gear R3, which is the third speed forward rotation faster than the second speed rotation. Is output to the output gear 50.

  In the fourth speed of the drive range, the clutch C1 and the brake B2 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the carriers CR2 and CR3 via the clutch C1, and the rotation of the sun gear S2 is prevented as the brake B2 is engaged.

  Therefore, the rotation of the input shaft 20 input to the carriers CR2 and CR3 is decelerated by the fixed sun gear S2, and is output to the ring gear R3. The rotation in the positive direction of the fourth speed faster than the rotation of the third speed is the output gear. 50 is output.

  In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, and output to the ring gear R1, but since the clutch C3 is released, the rotation to the sun gear S3 Is not transmitted.

  In the fifth speed of the drive range, the clutches C1 and C2 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the carriers CR2 and CR3 via the clutch C1 and to the ring gear R2 via the clutch C2, so that the planetary gear unit PR is directly connected.

  Then, the rotation of the input shaft 20 input to the carriers CR2 and CR3 is output to the ring gear R3 as it is, and the positive rotation of the fifth speed faster than the fourth speed is output to the output gear 50.

  In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, and output to the ring gear R1, but since the clutch C3 is released, the rotation to the sun gear S3 Is not transmitted.

  In the sixth speed of the drive range, the clutch C2 and the brake B2 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the ring gear R2 via the clutch C2, and the rotation of the sun gear S2 is blocked as the brake B2 is engaged.

  Accordingly, the rotation of the input shaft 20 input to the ring gear R2 is increased and output to the ring gear R3, and the 6th speed in the positive direction, which is faster than the 5th speed, is output to the output gear 50.

  In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, and output to the ring gear R1, but since the clutch C3 is released, the rotation to the sun gear S3 Is not transmitted.

  In the seventh speed of the drive range, the clutches C2 and C3 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the ring gear R2 via the clutch C2. In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, output to the ring gear R1, and input to the sun gear S3 via the clutch C3. Therefore, the rotation of the input shaft 20 input to the ring gear R2 is increased by the rotation input to the sun gear S3, and is output to the ring gear R3. The positive rotation of the seventh speed faster than the sixth speed is the output gear 50. Is output.

  In the eighth speed of the drive range, the clutch C2 and the brake B1 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the ring gear R2 via the clutch C2, and the rotation of the sun gear S3 is blocked as the brake B1 is engaged.

  Then, the rotation of the input shaft 20 input to the ring gear R2 is accelerated by the fixed sun gear S3 and output to the ring gear R3. The positive rotation of the eighth speed faster than the seventh speed is output to the output gear 50. Is done.

  In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, and output to the ring gear R1, but since the clutch C3 is released, the rotation to the sun gear S3 Is not transmitted.

  In the reverse range, the clutch C3 and the brake B3 are engaged.

  In this case, in the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, output to the ring gear R1, and output to the sun gear S3 via the clutch C3.

  Further, in the planetary gear unit PR, the rotation of the ring gear R2 is blocked with the engagement of the brake B3, and the rotation output to the sun gear S3 is reversed by the fixed ring gear R2 and output to the ring gear R3. The rotation in the direction is output to the output gear 50.

  In the parking range and the neutral range, the clutches C1 to C3 and the brakes B1 to B3 are disengaged and the power transmission between the input shaft 20 and the output gear 50 is cut off. become.

  Next, the velocity diagram in FIG. 3 will be described.

  In the speed diagram, the input / output state of the rotation with respect to the sun gears S1 to S3, the ring gears R1 to R3 and the carriers CR1 and CR2 for each shift stage in the transmission 11 is shown by straight lines, and the rotational speed is the position of each straight line. Indicated by The carrier CR3 is omitted because it is integral with the carrier CR2. The horizontal line n1 indicates that the rotational speed is zero (0), the horizontal line n2 indicates that the rotational speed is one time the rotational speed of the input shaft 20, and the horizontal line n3 indicates that the rotational speed is twice the rotational speed of the input shaft 20. Indicates that

  The vertical lines Y1 to Y3 indicate the carrier CR1, the ring gear R1, and the sun gear S1 in the planetary gear unit PF, and the vertical lines Y4 to Y8 indicate the sun gears S2, S3, the ring gears R2, R3, and the carrier CR2 in the planetary gear unit PR. In the present embodiment, the first to fifth rotating elements are constituted by the sun gears S2, S3, the ring gears R2, R3, and the carrier CR2.

  The interval between the vertical lines Y1 to Y3 is set based on the gear ratio λ1 of the planetary gear unit PF, and the interval between the vertical lines Y4 to Y8 is set based on the gear ratios λ2 and λ3 of the first and second planetary gear units G1 and G2. When the distance between the vertical lines Y1 and Y3 is 1, the distance between the vertical lines Y1 and Y2 is λ1, and when the distance between the vertical lines Y4 and Y8 is 1, the distance between the vertical lines Y6 and Y8 is When the distance is λ2 and the distance between the vertical lines Y5 and Y8 is 1, the distance between the vertical lines Y7 and Y8 is λ3.

  Further, m1 to m8 are 1st to 8th speed lines, and mr is a reverse range speed line. In 1st speed, the rotation speed of the carrier CR2 is the rotation speed of the input shaft 20, and the rotation speed of the ring gear R2 is zero. In the second speed, the rotation speed of the carrier CR2 is set to the rotation speed of the input shaft 20, the rotation speed of the sun gear S3 is set to zero, and in the third speed, the rotation speed of the carrier CR2 is set to the rotation speed of the input shaft 20. The rotational speed of S3 is the rotational speed of the ring gear R1, the rotational speed of the carrier CR2 is the rotational speed of the input shaft 20 at the 4th speed, the rotational speed of the sun gear S2 is zero, and the 5th speed is the carrier CR2 and the ring gear R2. Is set to the rotational speed of the input shaft 20, and at the sixth speed, the rotational speed of the ring gear R2 is set to the rotational speed of the input shaft 20, and the rotational speed of the sun gear S2 is set to In the seventh speed, the rotational speed of the ring gear R2 is set to the rotational speed of the input shaft 20, the rotational speed of the sun gear S3 is set to the rotational speed of the ring gear R1, and in the eighth speed, the rotational speed of the ring gear R2 is set to the rotational speed of the input shaft 20. In the reverse range, the rotational speed of the ring gear R2 is made zero, and the rotational speed of the sun gear S3 is made the rotational speed of the ring gear R1.

  Thus, in the present embodiment, the first to eighth gears can be achieved by engaging and disengaging the clutches C1 to C3 and the brakes B1 to B3. The number of components can be increased, and the size and weight of the transmission 11 are not increased.

  Next, a second embodiment of the present invention will be described. In addition, about the thing which has the same structure as 1st Embodiment, the description is abbreviate | omitted by providing the same code | symbol, and the effect of the same embodiment is used about the effect of the invention by having the same structure. .

  FIG. 4 is a schematic diagram of the transmission according to the second embodiment of the present invention, FIG. 5 is a diagram showing an operation table of the transmission according to the second embodiment of the present invention, and FIG. 6 is the second diagram of the present invention. It is a speed diagram of the transmission in an embodiment.

  In this case, in the planetary gear unit PF as the first transmission unit and as the differential rotation device, the sun gear S1 is selectively connected to the input shaft 20 as the input member via the clutch C3, and the ring gear R1 is It is connected to the sun gear S3 as the second differential rotation element, and is selectively connected to the transmission case 10 as the casing and as the non-rotating member via the brake B1, and the carrier CR1 is a transmission. It is connected and fixed to the case 10, and is selectively connected to the sun gear S2 as the first differential rotation element via the brake B2. The sun gear S1, the ring gear R1, and the carrier CR1 constitute first to third differential rotation elements. The sun gear S1 functions as an input element, the ring gear R1 functions as an output element, and the carrier CR1 functions as a fixed element. The clutch C3 and the brakes B1 and B2 constitute a friction engagement element, the clutch C3 constitutes a third clutch, and the brakes B1 and B2 constitute a first brake and a second brake.

  When the clutch C3 is engaged in the third and seventh speeds of the drive range and the reverse range, the rotation of the input shaft 20 is input to the sun gear S1 and decelerated by the fixed carrier CR1 to be ring gear R1. To the sun gear S3.

  Next, a third embodiment of the present invention will be described. In addition, about the thing which has the same structure as 1st Embodiment, the description is abbreviate | omitted by providing the same code | symbol, and the effect of the same embodiment is used about the effect of the invention by having the same structure. .

  FIG. 7 is a schematic diagram of the transmission according to the third embodiment of the present invention, FIG. 8 is a diagram showing an operation table of the transmission according to the third embodiment of the present invention, and FIG. 9 is the third diagram of the present invention. It is a speed diagram of the transmission in an embodiment.

  In this case, the planetary gear unit PR as the second transmission unit includes a sun gear S2 as a first differential rotation element, S3 as a second differential rotation element, a ring gear R2 as a third differential rotation element, Ring gear R3 as a fourth differential rotation element, pinion P2a meshing with sun gear S2, pinion P2b meshing with ring gear R2 and pinion P2a, pinion P3 meshing with sun gear S3, and fifth differential rotation element Carrier CR2 and CR3, and the carrier CR2 supports the pinions P2a and P2b, and the carrier CR3 supports the pinion P3.

  The sun gear S2 functions as an input element, the sun gear S3 functions as a fixed element, the ring gear R2 functions as an input element or fixed element, the ring gear R3 functions as an output element, and the carriers CR2 and CR3 function as input elements or fixed elements. A long pinion formed integrally with the pinions P2b and P3 is formed, and a short pinion is formed with the pinion P2a. The pinion P2a functions as a first transmission element, and the pinions P2b and P3 function as a second transmission element. The first planetary gear unit G1 as the first differential rotation device is a second planetary gear unit G2 as a second differential rotation device by a sun gear S2, a ring gear R2, pinions P2a and P2b, and a carrier CR2. Is constituted by a sun gear S3, a ring gear R3, a pinion P3 and a carrier CR3.

  In the planetary gear unit PF, the sun gear S1 as the first differential rotation element is connected to the input shaft 20 as the input member, and the ring gear R1 as the second differential rotation element is connected to the carrier via the clutch C3. The carrier CR1 as a third differential rotating element is selectively connected to CR2 and CR3, and is connected and fixed to a transmission case 10 as a casing and as a non-rotating member. The sun gear S1 forms an input element, the ring gear R1 forms an output element, and the carrier CR1 forms a fixed element.

  In the planetary gear unit PR, the sun gear S2 is selectively connected to the input shaft 20 via a clutch C1, and the ring gear R2 is a transmission that is connected to the input shaft 20 via a clutch C2 and via a brake B3. The sun gear S3 is selectively connected to the transmission case 10 via the brake B2, and the ring gear R3 is connected to the output gear 50 via the output shaft 12 as an output member. CR2 and CR3 are connected to each other, and selectively connected to the ring gear R1 via the clutch C3 and to the transmission case 10 via the brake B1. The clutches C1 to C3 and the brakes B1 to B3 constitute a friction engagement element, the clutches C1 to C3 constitute a first clutch to a third clutch, and the brakes B1 to B3 constitute a first brake to a third brake.

  Next, the operation of the transmission 11 will be described according to the operation table of FIG.

  First, in the first speed of the drive range, the clutch C1 and the brake B3 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the sun gear S2 via the clutch C1, and the rotation of the ring gear R2 is blocked as the brake B3 is engaged.

  Accordingly, the rotation of the input shaft 20 input to the sun gear S2 is decelerated while the carriers CR2, CR3 and the sun gear S3 are idled in the reverse direction by the fixed ring gear R2, and is output to the ring gear R3 to be output to the first gear. The rotation in the direction is output to the output gear 50.

  In the planetary gear unit PF as the first transmission unit and as the differential rotation device, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, and output to the ring gear R1. However, since the clutch C3 is released, it is not transmitted to the carriers CR2 and CR3.

  In the second speed of the drive range, the clutch C1 and the brake B1 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the sun gear S2 via the clutch C1, and the rotation of the carriers CR2 and CR3 is blocked as the brake B1 is engaged.

  As a result, the rotation of the input shaft 20 input to the sun gear S2 is decelerated by the fixed carriers CR2 and CR3, and is output to the ring gear R3, and the second-speed positive rotation faster than the first-speed rotation is output. It is output to the gear 50.

  In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, and output to the ring gear R1, but since the clutch C3 is released, the carrier CR2, It is not transmitted to CR3.

  In the third speed of the drive range, the clutches C1 and C3 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the sun gear S2 via the clutch C1. In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, output to the ring gear R1, and input to the carriers CR2 and CR3 via the clutch C3. Therefore, the rotation of the input shaft 20 input to the sun gear S2 is further decelerated by the rotation input to the carriers CR2 and CR3, and is output to the ring gear R3, which is the third speed forward rotation faster than the second speed rotation. Is output to the output gear 50.

  In the fourth speed of the drive range, the clutch C1 and the brake B2 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the sun gear S2 via the clutch C1, and the rotation of the sun gear S3 is blocked as the brake B2 is engaged.

  Therefore, the rotation of the input shaft 20 input to the sun gear S2 is decelerated by the fixed sun gear S3 and output to the ring gear R3, and the forward rotation of the fourth speed, which is faster than the third speed, is applied to the output gear 50. Is output.

  In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, and output to the ring gear R1, but since the clutch C3 is released, the carrier CR2, It is not transmitted to CR3.

  In the fifth speed of the drive range, the clutches C1 and C2 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the sun gear S2 via the clutch C1 and to the ring gear R2 via the clutch C2, so that the planetary gear unit PR is directly connected.

  Then, the rotation of the input shaft 20 input to the sun gear S2 and the ring gear R2 is output to the ring gear R3 as it is, and the rotation in the positive direction of the fifth speed faster than the fourth speed is output to the output gear 50.

  In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, and output to the ring gear R1, but since the clutch C3 is released, the carrier CR2, It is not transmitted to CR3.

  In the sixth speed of the drive range, the clutch C2 and the brake B2 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the ring gear R2 via the clutch C2, and the rotation of the sun gear S3 is blocked as the brake B2 is engaged.

  Accordingly, the rotation of the input shaft 20 input to the ring gear R2 is increased and output to the ring gear R3, and the 6th speed in the positive direction, which is faster than the 5th speed, is output to the output gear 50.

  In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, and output to the ring gear R1, but since the clutch C3 is released, the carrier CR2, It is not transmitted to CR3.

  In the seventh speed of the drive range, the clutches C2 and C3 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the ring gear R2 via the clutch C2. In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, output to the ring gear R1, and input to the carriers CR2 and CR3 via the clutch C3. Therefore, the rotation of the input shaft 20 input to the ring gear R2 is increased by the rotation input to the carriers CR2 and CR3, and is output to the ring gear R3, and the forward rotation of the 7th speed faster than the 6th speed is output. It is output to the gear 50.

  In the eighth speed of the drive range, the clutch C2 and the brake B1 are engaged. In this case, in the planetary gear unit PR, the rotation of the input shaft 20 is input to the ring gear R2 via the clutch C2, and the rotation of the carriers CR2 and CR3 is blocked as the brake B1 is engaged.

  Then, the rotation of the input shaft 20 input to the ring gear R2 is accelerated by the fixed carriers CR2 and CR3 and output to the ring gear R3, and the forward rotation of the eighth speed faster than the seventh speed is the output gear 50. Is output.

  In the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, and output to the ring gear R1, but since the clutch C3 is released, the carrier CR2, It is not transmitted to CR3.

  In the reverse range, the clutch C3 and the brake B3 are engaged.

  In this case, in the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, output to the ring gear R1, and output to the carriers CR2 and CR3 via the clutch C3. .

  Further, in the planetary gear unit PR, the rotation of the ring gear R2 is prevented with the engagement of the brake B3, and the rotation output to the carriers CR2 and CR3 is reversed by the fixed ring gear R2 and output to the ring gear R3. The rotation in the reverse direction is output to the output gear 50.

  In the parking range and the neutral range, the clutches C1 to C3 and the brakes B1 to B3 are disengaged and the power transmission between the input shaft 20 and the output gear 50 is cut off. become.

  Next, the velocity diagram in FIG. 9 will be described.

  In the speed diagram, the input / output state of the rotation with respect to the sun gears S1 to S3, the ring gears R1 to R3 and the carriers CR1 and CR2 for each shift stage in the transmission 11 is shown by straight lines, and the rotational speed is the position of each straight line. Indicated by The carrier CR3 is omitted because it is integral with the carrier CR2. The horizontal line n1 indicates that the rotational speed is zero, the horizontal line n2 indicates that the rotational speed is one time the rotational speed of the input shaft 20, and the horizontal line n3 indicates that the rotational speed is twice the rotational speed of the input shaft 20. Indicates.

  In this case, vertical lines Y1 to Y3 indicate the carrier CR1, ring gear R1, and sun gear S1 in the planetary gear unit PF, and vertical lines Y4 to Y8 indicate the sun gear S3, carrier CR2, ring gears R2, R3, and sun gear S2 in the planetary gear unit PR. . In the present embodiment, the first to fifth rotating elements are constituted by the sun gear S3, the carrier CR2, the ring gears R2, R3, and the sun gear S2.

  The intervals between the vertical lines Y1 to Y3 are set based on the gear ratio λ1 of the planetary gear unit PF, and the intervals between the vertical lines Y4 to Y8 are set based on the gear ratios λ2 and λ3 of the first and second planetary gear units G1 and G2. When the distance between the vertical lines Y1 and Y3 is 1, the distance between the vertical lines Y1 and Y2 is λ1, and when the distance between the vertical lines Y5 and Y8 is 1, the distance between the vertical lines Y5 and Y6. When the distance is λ2 and the distance between the vertical lines Y4 and Y5 is 1, the distance between the vertical lines Y5 and Y7 is λ3.

  Further, m1 to m8 are 1st to 8th speed lines, and mr is a reverse range speed line. In 1st speed, the rotational speed of the sun gear S2 is the rotational speed of the input shaft 20, and the rotational speed of the ring gear R2 is zero. In the second speed, the rotational speed of the sun gear S2 is set to the rotational speed of the input shaft 20, the rotational speed of the carrier CR2 is set to zero, and in the third speed, the rotational speed of the sun gear S2 is set to the rotational speed of the input shaft 20. The rotational speed of CR2 is set to the rotational speed of the ring gear R1, the rotational speed of the sun gear S2 is set to the rotational speed of the input shaft 20 at the fourth speed, the rotational speed of the sun gear S3 is set to zero, and the sun gear S2 and the ring gear R2 at the fifth speed. , The rotational speed of the ring gear R2 is set to the rotational speed of the input shaft 20 and the rotational speed of the sun gear S3 is set to zero at the sixth speed. In the seventh speed, the rotational speed of the ring gear R2 is set to the rotational speed of the input shaft 20, the rotational speed of the carrier CR2 is set to the rotational speed of the ring gear R1, and in the eighth speed, the rotational speed of the ring gear R2 is set to the rotational speed of the input shaft 20. The rotation speed of the carrier CR2 is made zero, and in the reverse range, the rotation speed of the ring gear R2 is made zero, and the rotation speed of the carrier CR2 is made the rotation speed of the ring gear R1.

  Next, a fourth embodiment of the present invention will be described. In addition, about the thing which has the same structure as 3rd Embodiment, the description is abbreviate | omitted by providing the same code | symbol, and the effect of the embodiment is used about the effect of the invention by having the same structure. .

  FIG. 10 is a schematic diagram of the transmission according to the fourth embodiment of the present invention, FIG. 11 is a diagram showing an operation table of the transmission according to the fourth embodiment of the present invention, and FIG. 12 is the fourth diagram of the present invention. It is a speed diagram of the transmission in an embodiment.

  In this case, in the planetary gear unit PF as the first transmission unit and as the differential rotation device, the sun gear S1 is connected to the input shaft 20 as the input member, and the ring gear R1 is used as the fifth differential rotation element. And a carrier case CR2 and CR3 as second rotating elements, and the carrier CR1 as a casing and a transmission case 10 as a non-rotating member via a brake B4 as a friction engagement element Selectively linked. The sun gear S1, the ring gear R1 and the carrier CR1 constitute first to third differential rotation elements. The input element representing the rotation element by the sun gear S1 is the output element representing the rotation element by the ring gear R1. The carrier CR1 constitutes a fixed element that represents the rotating element. Further, the brake B4 constitutes a fourth brake.

  In the third and seventh speeds of the drive range and the reverse range, the brake B4 is engaged to prevent the carrier CR1 from rotating. Therefore, in the planetary gear unit PF, the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed carrier CR1, output to the ring gear R1, and input to the carriers CR2 and CR3.

  Thus, in the present embodiment, the first to eighth gears can be achieved by engaging and disengaging the clutches C1 and C2 and the brakes B1 to B4 as the friction engagement elements. The number of gears to be increased can be increased, the number of parts can be reduced, and the size and weight can be reduced.

  Next, a fifth embodiment of the present invention will be described. In addition, about the thing which has the same structure as 3rd Embodiment, the description is abbreviate | omitted by providing the same code | symbol, and the effect of the embodiment is used about the effect of the invention by having the same structure. .

  FIG. 13 is a schematic diagram of the transmission according to the fifth embodiment of the present invention, FIG. 14 is a diagram showing an operation table of the transmission according to the fifth embodiment of the present invention, and FIG. 15 is the fifth embodiment of the present invention. It is a speed diagram of the transmission in an embodiment.

  In this case, in the planetary gear unit PF as the first transmission unit and as the differential rotation device, the sun gear S1 is connected and fixed to the transmission case 10 as the casing and as the non-rotating member. The ring gear R1 is connected to the carriers CR2 and CR3 as the frictional engagement element and as the fifth differential rotation element and as the second rotation element via the clutch C3 as the third clutch, The carrier CR1 is connected to an input shaft 20 as an input member. The sun gear S1, the ring gear R1, and the carrier CR1 constitute first to third differential rotation elements, and the input element that represents the rotation element by the carrier CR1 and the output element that represents the rotation element by the ring gear R1, The sun gear S1 constitutes a fixed element that represents a rotating element.

  In the third and seventh speeds of the drive range and the reverse range, the rotation of the input shaft 20 is input to the carrier CR1, decelerated by the fixed sun gear S1, and output to the ring gear R1, via the clutch C3. It is input to carriers CR2 and CR3.

  Next, a sixth embodiment of the present invention will be described. In addition, about the thing which has the same structure as 3rd Embodiment, the description is abbreviate | omitted by providing the same code | symbol, and the effect of the embodiment is used about the effect of the invention by having the same structure. .

  FIG. 16 is a schematic diagram of a transmission apparatus according to the sixth embodiment of the present invention, FIG. 17 is a diagram showing an operation table of the transmission apparatus according to the sixth embodiment of the present invention, and FIG. It is a speed diagram of the transmission in an embodiment.

  In this case, in the planetary gear unit PF as the first transmission unit and as the differential rotation device, the sun gear S1 serves as a casing as a friction engagement element and via a brake B4 as the fourth brake. And a transmission case 10 as a non-rotating member, and the ring gear R1 is connected to carriers CR2 and CR3 as a fifth differential rotating element and as a second rotating element, The carrier CR1 is connected to an input shaft 20 as an input member. The sun gear S1, the ring gear R1, and the carrier CR1 constitute first to third differential rotation elements, and the input element that represents the rotation element by the carrier CR1 and the output element that represents the rotation element by the ring gear R1, The sun gear S1 constitutes a fixed element that represents a rotating element.

  In the third and seventh speeds of the drive range and the reverse range, the brake B4 is engaged to prevent the sun gear S1 from rotating. Therefore, in the planetary gear unit PF, when the rotation of the input shaft 20 is input to the carrier CR1, it is decelerated by the fixed sun gear S1, output to the ring gear R1, and input to the carriers CR2 and CR3.

  Next, a seventh embodiment of the present invention will be described. In addition, about the thing which has the same structure as 3rd Embodiment, the description is abbreviate | omitted by providing the same code | symbol, and the effect of the embodiment is used about the effect of the invention by having the same structure. .

  FIG. 19 is a schematic diagram of the transmission according to the seventh embodiment of the present invention, FIG. 20 is a diagram showing an operation table of the transmission according to the seventh embodiment of the present invention, and FIG. 21 is the seventh diagram of the present invention. It is a speed diagram of the transmission in an embodiment.

  In this case, in the planetary gear unit PF as the first transmission unit and as the differential rotation device, the sun gear S1 serves as a friction engagement element and as an input member via a clutch C3 as a third clutch. The ring gear R1 is connected as a fifth differential rotation element and carriers CR2 and CR3 as second rotation elements, and the carrier CR1 as a housing and The transmission case 10 as a non-rotating member is connected and fixed. The sun gear S1, the ring gear R1 and the carrier CR1 constitute first to third differential rotation elements, the input element representing the rotation element by the sun gear S1, and the output element representing the rotation element by the ring gear R1, The carrier CR1 constitutes a fixed element that represents a rotating element.

  Then, in the third and seventh speeds of the drive range and the reverse range, the clutch C3 is engaged, and the rotation of the input shaft 20 is input to the sun gear S1 and decelerated by the fixed carrier CR1 to be ring gear R1. To the carriers CR2 and CR3.

  Next, an eighth embodiment of the present invention will be described. In addition, about the thing which has the same structure as 3rd Embodiment, the description is abbreviate | omitted by providing the same code | symbol, and the effect of the embodiment is used about the effect of the invention by having the same structure. .

  FIG. 22 is a schematic diagram of the transmission according to the eighth embodiment of the present invention, FIG. 23 is a diagram showing an operation table of the transmission according to the eighth embodiment of the present invention, and FIG. 24 is the eighth embodiment of the present invention. It is a speed diagram of the transmission in an embodiment.

  In this case, in the planetary gear unit PF as the first transmission unit and as the differential rotation device, the sun gear S1 is connected and fixed to the transmission case 10 as the housing and as the non-rotating member, The ring gear R1 is connected to the carriers CR2 and CR3 as the fifth differential rotation element and the second rotation element, and the carrier CR1 has the clutch C3 as the friction engagement element and the third clutch. Via the input shaft 20 as an input member. The sun gear S1, the ring gear R1, and the carrier CR1 constitute first to third differential rotation elements, and the input element that represents the rotation element by the carrier CR1 and the output element that represents the rotation element by the ring gear R1, The sun gear S1 constitutes a fixed element that represents a rotating element.

  In the third and seventh speeds of the drive range and in the reverse range, the clutch C3 is engaged, and the rotation of the input shaft 20 is input to the carrier CR1 and decelerated by the fixed sun gear S1 to be ring gear R1. To the carriers CR2 and CR3.

  Next, a ninth embodiment of the present invention will be described. In addition, about the thing which has the same structure as 3rd Embodiment, the description is abbreviate | omitted by providing the same code | symbol, and the effect of the embodiment is used about the effect of the invention by having the same structure. .

  FIG. 25 is a schematic diagram of the transmission according to the ninth embodiment of the present invention, FIG. 26 is a diagram showing an operation table of the transmission according to the ninth embodiment of the present invention, and FIG. 27 is the ninth embodiment of the present invention. It is a speed diagram of the transmission in an embodiment.

  In this case, in the planetary gear unit PF as the first transmission unit and as the differential rotation device, the sun gear S1 is connected to the input shaft 20 as the input member, and the ring gear R1 is as the housing and non-rotating The carrier CR1 is connected and fixed to the transmission case 10 as a member, and the carrier CR1 is used as a fifth differential rotation element as a friction engagement element and as a fifth differential rotation element via a clutch C3 as a third clutch. Are selectively connected to carriers CR2 and CR3 as rotating elements. The sun gear S1, the ring gear R1 and the carrier CR1 constitute first to third differential rotation elements. The input element representing the rotation element by the sun gear S1 is an output element representing the rotation element by the carrier CR1. The ring gear R1 constitutes a fixed element that represents a rotating element.

  Then, in the third and seventh speeds of the drive range and the reverse range, the clutch C3 is engaged, and the rotation of the input shaft 20 is input to the sun gear S1 and decelerated by the fixed ring gear R1 to be carrier CR1. And input to the carriers CR2 and CR3 via the clutch C3.

  Next, a tenth embodiment of the present invention will be described. In addition, about the thing which has the same structure as 3rd Embodiment, the description is abbreviate | omitted by providing the same code | symbol, and the effect of the embodiment is used about the effect of the invention by having the same structure. .

  FIG. 28 is a schematic diagram of the transmission in the tenth embodiment of the present invention, FIG. 29 is a diagram showing an operation table of the transmission in the tenth embodiment of the present invention, and FIG. 30 is the tenth embodiment of the present invention. It is a speed diagram of the transmission in an embodiment.

  In this case, in the planetary gear unit PF as the first transmission unit and as the differential rotation device, the sun gear S1 is connected to the input shaft 20 as the input member, the ring gear R1 as the friction engagement element, and The carrier CR1 is selectively connected to the transmission case 10 as the casing and as the non-rotating member via the brake B4 as the fourth brake, and the carrier CR1 serves as the fifth differential rotation element and the second Are connected to carriers CR2 and CR3 as rotating elements. The sun gear S1, the ring gear R1 and the carrier CR1 constitute first to third differential rotation elements. The input element representing the rotation element by the sun gear S1 is an output element representing the rotation element by the carrier CR1. The ring gear R1 constitutes a fixed element that represents a rotating element.

  Then, in the third and seventh speeds of the drive range and the reverse range, the brake B4 is engaged, and the rotation of the input shaft 20 is input to the sun gear S1 and decelerated by the fixed ring gear R1, and then the carrier CR1. To the carriers CR2 and CR3.

  Next, an eleventh embodiment of the present invention will be described. In addition, about the thing which has the same structure as 3rd Embodiment, the description is abbreviate | omitted by providing the same code | symbol, and the effect of the embodiment is used about the effect of the invention by having the same structure. .

  FIG. 31 is a schematic diagram of the transmission according to the eleventh embodiment of the present invention, FIG. 32 is a diagram showing an operation table of the transmission according to the eleventh embodiment of the present invention, and FIG. 33 is the eleventh of the present invention. It is a speed diagram of the transmission in an embodiment.

  In this case, in the planetary gear unit PF as the first transmission unit and as the differential rotation device, the sun gear S1 serves as the friction engagement element and serves as the input member via the clutch C3 as the third clutch. The input gear 20 is selectively connected, the ring gear R1 is connected and fixed as a housing and a transmission case 10 as a non-rotating member, the carrier CR1 is used as a fifth differential rotating element, and Are coupled to carriers CR2 and CR3 as second rotating elements. The sun gear S1, the ring gear R1 and the carrier CR1 constitute first to third differential rotation elements. The input element representing the rotation element by the sun gear S1 is an output element representing the rotation element by the carrier CR1. The ring gear R1 constitutes a fixed element that represents a rotating element.

  Then, in the third and seventh speeds of the drive range and the reverse range, the clutch C3 is engaged, and the rotation of the input shaft 20 is input to the sun gear S1, decelerated by the fixed ring gear R1, and then the carrier CR1. To the carriers CR2 and CR3.

  In addition, this invention is not limited to the said embodiment, It can change variously based on the meaning of this invention, and does not exclude them from the scope of the present invention.

It is a schematic diagram of the transmission in the first embodiment of the present invention. It is a figure which shows the action | operation table | surface of the transmission in the 1st Embodiment of this invention. It is a speed diagram of the transmission in the 1st Embodiment of this invention. It is a schematic diagram of the transmission in the 2nd Embodiment of this invention. It is a figure which shows the action | operation table | surface of the transmission in the 2nd Embodiment of this invention. It is a speed diagram of the transmission in the 2nd Embodiment of this invention. It is a schematic diagram of the transmission in the 3rd Embodiment of this invention. It is a figure which shows the action | operation table | surface of the transmission in the 3rd Embodiment of this invention. It is a speed diagram of the transmission in the 3rd Embodiment of this invention. It is a schematic diagram of the transmission in the 4th Embodiment of this invention. It is a figure which shows the action | operation table | surface of the transmission in the 4th Embodiment of this invention. It is a speed diagram of the transmission in the 4th Embodiment of this invention. It is a schematic diagram of the transmission in the 5th Embodiment of this invention. It is a figure which shows the action | operation table | surface of the transmission in the 5th Embodiment of this invention. It is a speed diagram of the transmission in the 5th Embodiment of this invention. It is a schematic diagram of the transmission in the 6th Embodiment of this invention. It is a figure which shows the action | operation table | surface of the transmission in the 6th Embodiment of this invention. It is a speed diagram of the transmission in the 6th Embodiment of this invention. It is a schematic diagram of the transmission in the 7th Embodiment of this invention. It is a figure which shows the action | operation table | surface of the transmission in the 7th Embodiment of this invention. It is a speed diagram of the transmission in the 7th Embodiment of this invention. It is a schematic diagram of the transmission in the 8th Embodiment of this invention. It is a figure which shows the action | operation table | surface of the transmission in the 8th Embodiment of this invention. It is a speed diagram of the transmission in the 8th Embodiment of this invention. It is a schematic diagram of the transmission in the ninth embodiment of the present invention. It is a figure which shows the action | operation table | surface of the transmission in the 9th Embodiment of this invention. It is a speed diagram of the transmission in the ninth embodiment of the present invention. It is a schematic diagram of the transmission in the tenth embodiment of the present invention. It is a figure which shows the action | operation table | surface of the transmission in the 10th Embodiment of this invention. It is a speed diagram of the transmission in the tenth embodiment of the present invention. It is a schematic diagram of the transmission in the eleventh embodiment of the present invention. It is a figure which shows the action | operation table | surface of the transmission in the 11th Embodiment of this invention. It is a speed diagram of the transmission in the eleventh embodiment of the present invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Transmission case 11 Transmission 20 Input shaft B1-B4 Brake C1-C3 Clutch CR1-CR3 Carrier G1, G2 1st, 2nd planetary gear unit PF, PR Planetary gear unit R1-R3 Ring gear S1-S3 Sun gear

Claims (9)

  A first transmission unit comprising a rotating element to which rotation of an input member is input, a rotating element fixed to a non-rotating member, and a rotating element that outputs rotation, and an input / output state of rotation In the velocity diagram representing the above, the first to fifth rotating elements are provided from one end to the other end, and the second shifting section is composed of a plurality of differential rotating devices. In a transmission device that changes the speed of at least seven of the eight shift stages by changing the input / output state of the rotation for each rotary element, the rotation of each shift stage from the fourth rotary element is the output member. In the first speed, the rotation of the input member is input to the fifth rotating element, the third rotating element is connected to the non-rotating member, and the second rotating element is connected to the fifth rotating element in the second speed. Rotation input, second rotation required Is connected to the non-rotating member, and at the third speed, the rotation of the input member is input to the fifth rotating element, the rotation of the first transmission unit is input to the second rotating element, and at the fourth speed, The rotation of the input member is input to the rotation element 5, the first rotation element is connected to the non-rotation member, and the rotation of the input member is input to the third and fifth rotation elements at the fifth speed, 6 At the speed, the rotation of the input member is input to the third rotating element, the first rotating element is connected to the non-rotating member, and at the seventh speed, the rotation of the input member is input to the third rotating element, The rotation of the first transmission unit is input to the second rotation element, the rotation of the input member is input to the third rotation element at the eighth speed, and the second rotation element is connected to the non-rotation member. A transmission characterized by that.   The transmission according to claim 1, wherein the rotation of the first transmission unit is output as a predetermined friction engagement element is engaged.   The transmission according to claim 2, wherein the friction engagement element is disposed between the first and second transmission units.   The transmission according to claim 2, wherein the friction engagement element is disposed between the first transmission unit and the input member.   The transmission according to claim 2, wherein the friction engagement element is disposed between the first transmission unit and the non-rotating member.   The second transmission unit includes first and second differential rotating devices, and the first to fifth rotating elements are a sun gear of the first differential rotating device and a sun gear of the second differential rotating device. The transmission according to claim 1, wherein the transmission is a carrier common to the ring gear of the first differential rotation device, the ring gear of the second differential rotation device, and the first and second differential rotation devices.   The second transmission unit includes first and second differential rotation devices, and the first to fifth rotation elements are sun gears of the second differential rotation device, and first and second differential rotation devices. The transmission according to claim 1, wherein the gear is a carrier common to the apparatus, a ring gear of the first differential rotation apparatus, a ring gear of the second differential rotation apparatus, and a sun gear of the first differential rotation apparatus.   1st clutch-3rd clutch arrange | positioned between the said rotation elements, and 1st brake-3rd brake arrange | positioned between the said rotation element and a non-rotating member, The said 1st clutch is 1st speed. The second clutch is engaged at 5th to 8th speed, the third clutch is engaged at 3rd and 7th speed, and the first brake is at 2nd and 8th speed. The transmission according to claim 1, wherein the second brake is engaged at the fourth speed and the sixth speed, and the third brake is engaged at the first speed. The first clutch and the second clutch disposed between the rotating elements, and the first brake to the fourth brake disposed between the rotating element and the non-rotating member, wherein the first clutch is a first speed. The second clutch is engaged at 5th to 8th speed, the first brake is engaged at 2nd and 8th speed, and the second brake is at 4th and 6th speed. The transmission according to claim 1, wherein the transmission is engaged, the third brake is engaged at the first speed, and the fourth brake is engaged at the third speed and the seventh speed.

Images