WO2024014119A1

WO2024014119A1 - Unit

Info

Publication number: WO2024014119A1
Application number: PCT/JP2023/018674
Authority: WO
Inventors: 和年下薗; 秀和八木
Original assignee: ジヤトコ株式会社
Priority date: 2022-07-13
Filing date: 2023-05-19
Publication date: 2024-01-18

Abstract

[Problem] To reduce the step ratio when shifting gears in a unit having a power transmission mechanism inside thereof. [Solution] This unit comprises an input element, an output element, first to third engagement elements, a first planetary gear mechanism with first to third rotating elements which are arranged in this order on a nomographic chart, and a second planetary gear mechanism with fourth to sixth rotating elements which are arranged in this order on the nomographic chart. The input element is connected to the fourth rotating element, the output element is connected to the third rotating element and the fifth rotating element, one side of the first engagement element is connected to the second rotating element and the sixth rotating element, the other side of the first engagement element is fixed, one side of the second engagement element is connected to the first rotating element, the other side of the second engagement element is fixed, and the third engagement element connects two rotating elements which are selected from the first to sixth rotating elements, and are not connected to each other.

Description

unit

The present invention relates to a unit having a power transmission mechanism inside.

Patent Document 1 discloses an automatic transmission unit for an electric vehicle with two forward speeds. In this unit, by switching the engagement state of the two friction clutches, it is possible to realize the first speed and the second speed, which has a smaller gear ratio (=input rotational speed/output rotational speed) than the first speed.

Similar units are also disclosed in Patent Documents 2 to 4.

German Patent No. 102019107517 German Patent Application No. 102019119947 German Patent Application No. 102019119949 China Utility Model No. 207333597

In an automatic transmission unit for an electric vehicle with two forward speeds, the torque amplification effect due to deceleration increases as the gear ratio of the first gear increases, so the maximum torque of the motor should be reduced as the gear ratio of the first gear increases. This allows you to select a motor with a small physique. On the other hand, as the gear ratio of the second speed is made smaller, the rotational speed of the motor to achieve a certain vehicle speed becomes lower, which is advantageous when cruising at high speed.

However, if the gear ratios of 1st and 2nd gear are set respectively based on the above design concept, the interstage ratio (=1st gear gear ratio/2nd gear gear ratio) when switching between 1st gear and 2nd gear becomes larger. , the acceleration/deceleration of the output rotation during gear shifting increases.

The present invention has been made in view of such technical problems, and an object of the present invention is to reduce the gear ratio during gear change in a unit having a power transmission mechanism inside.

According to an aspect of the invention, the unit includes:
an input element,
output element,
a first engagement element;
a second engagement element;
a third engagement element;
a first planetary gear mechanism in which a first rotating element, a second rotating element, and a third rotating element are arranged in this order on a collinear diagram;
and a second planetary gear mechanism in which a fourth rotational element, a fifth rotational element, and a sixth rotational element are arranged in this order on the collinear diagram.
the input element is connected to the fourth rotating element,
the output element is connected to the third rotation element and the fifth rotation element,
One side of the first engagement element is connected to the second rotation element and the sixth rotation element,
the other side of the first engagement element is fixed;
One side of the second engagement element is connected to the first rotating element,
the other side of the second engagement element is fixed;
The third engagement element connects two rotating elements selected from the first to sixth rotating elements that are not connected to each other.

According to the above aspect, three or more gear stages can be realized by changing the engagement states of the first to third engagement elements. As a result, the interstage ratio is smaller than that of a unit with two forward speeds, and the acceleration/deceleration of output rotation during shifting can be suppressed to be smaller than that of a unit with two forward speeds. Furthermore, a more appropriate gear ratio can be set for each gear.

Furthermore, when the first and second engagement elements are released and the third engagement element is engaged, the gear ratio becomes 1, and all the rotating elements that make up the first and second planetary gear mechanisms rotate at the same rotational speed. Therefore, power transmission loss caused by differential rotation between rotating elements can be reduced.

FIG. 1 is a skeleton diagram of a unit according to an embodiment of the present invention. FIG. 2 is an engagement table showing the engagement state of each engagement element at each gear stage. FIG. 3 is a collinear diagram of units. FIG. 4A is a skeleton diagram of a modified example of the unit. FIG. 4B is a skeleton diagram of a modified example of the unit. FIG. 4C is a skeleton diagram of a modified example of the unit.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. The definitions of terms used in this specification are as follows.

"Unit" means any device that has a power transmission mechanism inside, such as a gear mechanism or a differential gear mechanism, and includes a motor unit that has a motor and a power transmission mechanism, an automatic transmission unit, a reduction gear unit, etc. .

"Transmission ratio" is the value obtained by dividing the input rotational speed of the unit by the output rotational speed. "Input rotation" includes not only rotation input to the unit from a power source outside the unit, but also rotation input to the unit from a power source within the unit.

The "interstage ratio" is the value obtained by dividing the larger (low-speed) gear ratio by the smaller (high-speed) gear ratio of the two gear ratios realized by the unit.

"Axial direction" means the axial direction of the rotating shaft of the parts that make up the unit. The parts include motors, gear mechanisms, differential gear mechanisms, etc. "Radial direction" means the radial direction from the central axis of the rotating shaft.

"Housing" means a container that houses the motor, inverter, and power transmission mechanism, and is composed of one or more cases. A mode in which the case housing the motor, the case housing the inverter, and the case housing the power transmission mechanism are integrally formed is called "3in1."

"Motor" means a rotating electrical machine that has a motor function, and may have a generator function in addition to the motor function.

"Element A is connected to element B" means that element A is connected to upstream or downstream element B in such a manner that power can be transmitted between element A and element B. The power input side is upstream, and the power output side is downstream. The element A is not limited to being connected to the element B directly or via another member, but may be connected via a clutch or the like.

"Element A is fixed to element B" refers to both the manner in which element A is directly fixed to element B, and the manner in which element A is fixed to element B via element C other than element A and B. included. "Element A is fixed" means that element A is fixed to another element and cannot rotate.

"Element A and element B overlap when viewed in a predetermined direction" means that element A and element B are lined up in a predetermined direction (axial direction, radial direction, gravity direction, etc.), and when observed from the predetermined direction, element A and element B overlap. Refers to a state in which element B at least partially overlaps. This is synonymous with "element A and element B overlap in a predetermined direction". When element A and element B overlap in the axial direction, element A and element B are coaxial. When element A and element B are drawn side by side in a predetermined direction in the drawing, it means that element A and element B overlap when viewed in the predetermined direction.

On the other hand, "element A and element B do not overlap when viewed in a predetermined direction" means that element A and element B are not lined up in a predetermined direction (axial direction, radial direction, gravity direction, vehicle running direction, etc.). , refers to a state in which element A and element B do not have any overlapping portion when observed from a predetermined direction. This is synonymous with "element A and element B do not overlap in a predetermined direction". In the drawing, when element A and element B are drawn so as not to be lined up in a predetermined direction, it means that element A and element B do not overlap when viewed in the predetermined direction.

"Element A is located between element B and element C when viewed from a predetermined direction" means that element A is located between element B and element C when observed from a predetermined direction (axial direction, radial direction, gravity direction, etc.). means that something is observed. For example, when element B, element A, and element C are arranged in this order along the axial direction, element A is observed to be between element B and element C when viewed in the radial direction, so element A can be said to be located between element B and element C. Element A does not need to overlap elements B and C when viewed in the axial direction. When element A is drawn between elements B and C in the drawing, it means that element A is located between elements B and C when viewed in a predetermined direction.

"Arranged close to each other" means that two elements have a portion that overlaps with each other in an axial or radial view, and no other element is sandwiched between the two elements. . For example, "two engaging elements are arranged close to each other" means that a planetary gear mechanism or the like is not arranged between the two engaging elements. If no other element is drawn between element A and element B in the drawing, it means that element A and element B are arranged close to each other.

"One side of the engagement element" and "the other side of the engagement element" refer to an engagement element that is relatively non-rotatable when the engagement element is in the engaged state and becomes relatively rotatable when the engagement element is in the released state. means two elements contained in. "One side of the engagement element" and "the other side of the engagement element" may be a combination of rotating elements or a combination of a rotating element and a non-rotating element, and generally the former is called a clutch, and the latter is called a brake. Moreover, "one side of the engagement element" means either "one side of the engagement element" or "the other side of the engagement element".

Other terms will be defined as appropriate in the main text of the specification.

FIG. 1 is a skeleton diagram showing the basic structure of a unit 100 according to an embodiment of the present invention. The unit 100 is a forward drive unit for an electric vehicle that changes the rotation input from a motor as a power source (not shown) to an input element IN at a gear ratio corresponding to a gear position, and transmits it from an output element OUT to a drive wheel (not shown). It is a 3-speed automatic transmission unit. In this example, the input element IN is a rotating shaft and the output element OUT is a gear.

The unit 100 accommodates an input element IN, first and second planetary gear mechanisms PG1, PG2, first to third engagement elements B1, B2, CL, an output element OUT, and a motor and inverter (not shown) in a housing 1. It is a so-called 3-in-1 unit. The housing 1 is non-rotatably fixed to the vehicle.

One end of the input element IN is connected to the output shaft of the motor, and the input element IN is rotated by the power input from the motor. The rotational speed of the input element IN is the input rotational speed of the unit 100. The motor is electrically connected to a battery (not shown) outside the unit 100 via an inverter, and receives power from the battery to function as an electric motor. The motor can also function as a generator.

The first planetary gear mechanism PG1 includes a first sun gear S1 as a first rotating element, a plurality of first pinion gears (not shown), and a second rotating element that rotatably supports the plurality of first pinion gears. This is a single pinion planetary gear mechanism having a first carrier C1 and a first ring gear R1 as a third rotating element. The first sun gear S1 meshes with a plurality of first pinion gears, and the plurality of first pinion gears mesh with a first ring gear R1.

The second planetary gear mechanism PG2 includes a second sun gear S2 as a fourth rotating element, a plurality of second pinion gears (not shown), and a fifth rotating element that rotatably supports the plurality of second pinion gears. This is a single pinion planetary gear mechanism having two carriers C2 and a second ring gear R2 as a sixth rotating element. The second sun gear S2 meshes with a plurality of second pinion gears, and the plurality of second pinion gears mesh with a second ring gear R2.

The first carrier C1 is connected to the second ring gear R2. The first ring gear R1 is connected to the second carrier C2 and the output element OUT. The second sun gear S2 is connected to the input element IN.

The rotation speed of the output element OUT is the output rotation speed of the unit 100.

The first engagement element B1 is a brake. The first engagement element B1 is composed of a hydraulic or electric clutch. If the two parts of the first engaging element B1 that are to be engaged when the first engaging element B1 is brought into the engaged state are one side and the other side, one side is the first carrier C1 and the second part. It is connected to ring gear R2, and the other side is fixed to housing 1. Thereby, the first carrier C1 and the second ring gear R2 can be fixed to the housing 1 by engaging the first engagement element B1.

The second engagement element B2 is a brake. The second engagement element B2 is constituted by a hydraulic or electric clutch. If the two parts of the second engaging element B2 that are to be engaged when the second engaging element B2 is brought into the engaged state are one side and the other side, the one side is connected to the first sun gear S1. The other side is fixed to the housing 1. Thereby, the first sun gear S1 can be fixed to the housing 1 by engaging the second engagement element B2.

The third engagement element CL is a clutch. The third engagement element CL is composed of an electric multi-disc clutch.

The third engagement element CL includes a hub 11, inner friction plates 12 and outer friction plates 13 arranged alternately, a drum 14, and an electric actuator 15.

An inner friction plate 12 is spline-fitted to the outer periphery of the hub 11, and the inner friction plate 12 can be displaced relative to the hub 11 in the axial direction, but cannot rotate relative to the hub 11. Further, the hub 11 is spline-fitted to the input element IN, and cannot rotate relative to the input element IN.

The outer friction plate 13 is spline-fitted to the inner periphery of the drum 14, and the outer friction plate 13 can be displaced relative to the drum 14 but cannot rotate relative to the drum 14. Further, the drum 14 is connected to the output element OUT, the first ring gear R1, and the second carrier C2.

The electric actuator 15 is an actuator that drives the third engagement element CL. When the motor built in the electric actuator 15 is driven, the piston 15p is moved out in the axial direction, the inner friction plate 12 and the outer friction plate 13 are pressed against each other and become unable to rotate relative to each other, and the third engagement element CL is engaged. state. The electric actuator 15 mechanically applies force to the piston 15p and receives the reaction force from the piston 15p, so the electric actuator 15 is fixed to the housing 1.

Furthermore, when the motor built in the electric actuator 15 is driven in the opposite direction, the piston 15p retreats, the inner friction plate 12 and the outer friction plate 13 are separated, and the third engagement element CL is placed in a released state.

Note that instead of the electric actuator 15, it is also possible to use a hydraulic actuator that pushes out the piston 15p with hydraulic pressure. Oil may be supplied to the hydraulic actuator by a hydraulic supply unit attached to the housing 1 or the like, or by a control valve unit consisting of a spool, a solenoid valve, etc.

If the two parts of the third engaging element CL that are to be engaged when the third engaging element CL is brought into the engaged state are one side (hub 11) and the other side (drum 14), one side One side is connected to the input element IN and the second sun gear S2, and the other side is connected to the output element OUT, the first ring gear R1 and the second carrier C2. Accordingly, when the third engagement element CL is engaged, the input element IN and the second sun gear S2 are connected to the output element OUT, the first ring gear R1, and the second carrier C2.

By connecting the second sun gear S2 and the second carrier C2 with the third engagement element CL, the third engagement element CL is connected between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2. There is no need to arrange them, making layout design easier.

Actuators that can be used for the third engagement element CL include actuators that are subject to layout constraints (electric actuators that need to be fixed to the housing 1 etc. due to reaction force, and actuators that need to be attached to the housing 1 etc.) There are two types of actuators: hydraulic actuators, etc.) and actuators that are less subject to layout constraints (hydraulic actuators, etc. that supply hydraulic pressure from a control valve unit). When using the former actuator, if it is necessary to arrange the third engagement element CL between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2, the difficulty of layout design increases.

Regarding this point, with the arrangement shown in FIG. 1, layout design is easy regardless of the type of actuator, and the degree of freedom in selecting the actuator that drives the third engagement element CL can be increased.

Furthermore, by arranging the first planetary gear mechanism PG1 on one side of the second planetary gear mechanism PG2 in the axial direction and arranging the third engagement element CL on the other side of the second planetary gear mechanism PG2 in the axial direction, the first The planetary gear mechanism PG1 and the second planetary gear mechanism PG2 are arranged close to each other. This increases the degree of freedom in layout of other elements, and also allows the axial dimension of the unit 100 to be reduced.

Further, the third engagement element CL is arranged coaxially with the first and second planetary gear mechanisms PG1 and PG2, and includes a portion that overlaps with the first planetary gear mechanism PG1 and a second planetary gear mechanism when viewed in the axial direction. It has a portion that overlaps with gear mechanism PG2. This allows the radial dimension of the unit 100 to be reduced.

FIG. 2 is an engagement table showing the relationship between the engagement states of the first to third engagement elements B1, B2, and CL and the gears realized in the unit 100. In the table, black circles indicate engaged states, and blank circles indicate released states.

As shown in the engagement table, the first speed is achieved by engaging the first engagement element B1 and releasing the second and third engagement elements B2 and CL. The second speed is achieved by engaging the second engagement element B2 and releasing the first and third engagement elements B1 and CL. The third speed is achieved by engaging the third engagement element CL and releasing the first and second engagement elements B1 and B2.

Further, FIG. 3 is a collinear diagram of the unit 100. In the figure, vertical lines l1 to l4 correspond to each rotating element of the first and second planetary gear mechanisms PG1 and PG2, and regarding the first planetary gear mechanism PG1, from the left side of the figure, the first sun gear S1, the first carrier C1, The first ring gear R1 is lined up in this order, and regarding the second planetary gear mechanism PG2, the second sun gear S2, second carrier C2, and second ring gear R2 are lined up in this order from the right side in the figure.

Since the first carrier C1 and the second ring gear R2 are connected to each other, the same vertical line l2 corresponds to them. Similarly, since the first ring gear R1 and the second carrier C2 are also connected to each other, the same vertical line l3 corresponds to them. When the distance between vertical line l2 and vertical line l3 is 1, the distance between vertical line l1 and vertical line l2 and the distance between vertical line l3 and vertical line l4 are as follows: The number of teeth of first sun gear S1 is equal to the number of teeth of first ring gear R1. If the value divided by the number is α1, and the value obtained by dividing the number of teeth of the second sun gear S2 by the number of teeth of the second ring gear R2 is α2, then they become 1/α1 and 1/α2, respectively.

In the collinear diagram, straight lines L1 to L3 corresponding to each gear stage are drawn. The rotational speed of each rotating element is represented by the ordinate of the intersection of the straight lines L1 to L3 and the vertical lines l1 to l4 corresponding to each gear stage.

In the first speed, by engaging the first engagement element B1, the first carrier C1 and the second ring gear R2 are fixed to the housing 1, and the rotational speed of the first carrier C1 and the second ring gear R2 becomes zero. Therefore, the straight line L1 corresponding to the first speed is a straight line passing through the point X1.

If the rotational speed of the first ring gear R1 and the second carrier C2 is r1, and the rotational speed of the second sun gear S2 is r4, the input rotational speed rin of the unit 100 is equal to the rotational speed r4 of the second sun gear S2, and the output rotational speed rout is equal to the rotational speed r1 of the first ring gear R1 and the second carrier C2, so the gear ratio in the first speed is rin/rout=r4/r1.

In addition, in the second gear, the first sun gear S1 is fixed to the housing 1 by engaging the second engagement element B2, and the rotational speed of the first sun gear S1 becomes zero, so that the straight line corresponding to the second gear is L2 is a straight line passing through point X2.

If the rotational speed of the first ring gear R1 and the second carrier C2 is r2, and the rotational speed of the second sun gear S2 is r4, the input rotational speed rin of the unit 100 is equal to the rotational speed r4 of the second sun gear S2, and the output rotational speed rout is equal to the rotational speed r2 of the first ring gear R1 and the second carrier C2, so the gear ratio in second gear is rin/rout=r4/r2. Since r2 is larger than r1, the gear ratio of the second gear is smaller than the gear ratio of the first gear.

Furthermore, in the third speed, by engaging the third engagement element CL, the input element IN and the second sun gear S2 are connected to the output element OUT, the first ring gear R1, and the second carrier C2, so that each The rotational speeds of all rotating elements are equally r3. As a result, the input rotational speed rin and the output rotational speed rout also become equal, and the gear ratio in the third gear becomes 1, which is smaller than that in the second gear.

Therefore, in the unit 100, it is possible to realize three gear stages including the third gear with a gear ratio of 1, so the inter-stage ratio is smaller compared to a unit with two forward speeds, and the output rotation at the time of gear shifting is reduced. acceleration/deceleration can be kept smaller than that of a two-speed forward unit. Further, since the first to third speeds can be used for low speed, medium speed, and high speed, respectively, it is possible to set an appropriate gear ratio depending on the speed range.

Also, in 3rd speed, the gear ratio is 1. In other words, since all the rotating elements constituting the first and second planetary gear mechanisms PG1 and PG2 rotate at the same rotational speed, it is possible to reduce power transmission loss due to differential rotation between the rotating elements. In addition, since the input element IN and the output element OUT are connected, the power transmission path from the input element IN to the output element OUT becomes the shortest, and power transmission loss can be further reduced.

Next, a modification of the unit 100 will be described.

4A to 4C are skeleton diagrams of modified examples of the unit 100. The position of the third engagement element CL is different from the skeleton diagram shown in FIG. The same elements as in the skeleton diagram shown in FIG. 1 are given the same reference numerals.

Since the third engagement element CL only needs to be able to achieve a gear ratio of 1 by engaging, the position of the third engagement element CL may be other than the position shown in FIG. 1.

Specifically, in order to achieve a gear ratio of 1 in the collinear diagram shown in FIG. All you have to do is connect the rotating elements corresponding to the two selected ones.

In other words, from all combinations when selecting two rotating elements from the six rotating elements S1, C1, R1, S2, C2, and R2 of the first and second planetary gear mechanisms PG1 and PG2, the combinations that are already connected ( It is sufficient to select a combination of two rotating elements that are not connected to each other, excluding the first carrier C1 and second ring gear R2, or the first ring gear R1 and second carrier C2, and connect these two rotating elements.

In the modification shown in FIG. 4A, the third engagement element CL is arranged at a position where the input element IN and the second sun gear S2 can be connected to the first sun gear S1. Specifically, one side (hub 11) of the third engagement element CL is connected to the input element IN and the second sun gear S2, and the other side (drum 14) is connected to one side of the second engagement element B2 and the first sun gear S2. Connected to sun gear S1. The output element OUT is a rotating shaft.

This arrangement is suitable for a layout design in which the third engagement element CL is not arranged between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2. If the third engagement element CL is not disposed between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2, the degree of freedom in selecting the actuator that drives the third engagement element CL can be increased. I can do it.

The actuator for driving the third engagement element CL may be the same electric actuator 15 as the example shown in FIG. Actuators may also be used.

Furthermore, since the first to third engagement elements B1, B2, and CL can be arranged in one place, the distance between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2 can be reduced, etc. , the layout design of the first and second planetary gear mechanisms PG1 and PG2 becomes advantageous. Furthermore, by narrowing the distance between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2, there is more space around them, and the first to third engagement elements B1, B2, and CL can be placed in one place. It also becomes easier to secure space for arranging them all together.

Further, a second planetary gear mechanism PG2 is arranged on one side of the first planetary gear mechanism PG1 in the axial direction, and a third engagement element CL is arranged on the other side of the first planetary gear mechanism PG1 in the axial direction.

Since the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2 are arranged close to each other, the degree of freedom in layout of other elements is increased, and the axial dimension of the unit 100 can be reduced.

Moreover, since one side (drum 14) of the third engagement element CL and one side of the second engagement element B2 are connected, these can be made into a common part (integral part). Thereby, the number of parts of the unit 100 can be reduced.

In the modification shown in FIG. 4B, the third engagement element CL is arranged at a position where the input element IN and the second sun gear S2 can be connected to the first carrier C1 and the second ring gear R2. Specifically, one side (hub 11) of the third engagement element CL is connected to the input element IN and the second sun gear S2, and the other side (drum 14) is connected to one side of the first engagement element B1, the first It is connected to carrier C1 and second ring gear R2. The output rotation of the unit 100 is transmitted from an output element OUT connected to the first ring gear R1 and the second carrier C2 to a drive wheel (not shown). The output element OUT is a rotating shaft.

In this arrangement, the third engagement element CL is arranged between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2, so that the third engagement element CL can be used as an actuator for driving the third engagement element CL due to layout constraints. It is preferable to use a hydraulic actuator 16 that supplies hydraulic pressure from a control valve unit.

Moreover, since one side (drum 14) of the third engagement element CL and one side of the first engagement element B1 are connected, these can be made into a common part (integral part). Thereby, the number of parts of the unit 100 can be reduced.

In the modification shown in FIG. 4C, the third engagement element CL is arranged at a position where the input element IN and the second sun gear S2 can be connected to the first sun gear S1. Specifically, one side (hub 11) of the third engagement element CL is connected to the input element IN and the second sun gear S2, and the other side (drum 14) is connected to one side of the second engagement element B2 and the first sun gear S2. Connected to sun gear S1. The output rotation of the unit 100 is transmitted from an output element OUT connected to the first ring gear R1 and the second carrier C2 to a drive wheel (not shown). The output element OUT is a rotating shaft.

The engagement table and collinear diagram of the modified examples shown in FIGS. 4A to 4C are the same as those of the skeleton diagram of FIG. 1 shown in FIGS. 2 and 3.

Next, the effects of the embodiments of the present invention will be explained.

(1) The unit 100 according to the embodiment of the present invention is
input element IN;
Output element OUT and
A first engagement element B1;
a second engagement element B2;
a third engagement element CL;
A first planetary gear mechanism PG1 in which a first sun gear S1, a first carrier C1, and a first ring gear R1 are arranged in this order on a collinear diagram;
The second planetary gear mechanism PG2 includes a second sun gear S2, a second carrier C2, and a second ring gear R2 arranged in this order on the collinear diagram.
Input element IN is connected to second sun gear S2,
The output element OUT is connected to the first ring gear R1 and the second carrier C2,
One side of the first engagement element B1 is connected to the first carrier C1 and the second ring gear R2,
The other side of the first engagement element B1 is fixed,
One side of the second engagement element B2 is connected to the first sun gear S1,
The other side of the second engagement element B2 is fixed,
The third engagement element CL includes two rotating elements not connected to each other selected from the first sun gear S1, the first carrier C1, the first ring gear R1, the second sun gear S2, the second carrier C2, and the second ring gear R2. Connect elements.

According to this configuration, three or more gear stages can be realized by changing the engagement states of the first to third engagement elements B1, B2, and CL. As a result, the gear ratio is smaller than that of a unit with two forward speeds, and the acceleration/deceleration of output rotation during gear shifting can be suppressed to be smaller than that of a unit with two forward speeds. Furthermore, a more appropriate gear ratio can be set for each gear.

Furthermore, when the first and second engagement elements B1 and B2 are released and the third engagement element CL is engaged, the gear ratio becomes 1, and all the rotations constituting the first and second planetary gear mechanisms PG1 and PG2 are Since the elements rotate at the same rotational speed, power transmission loss due to differential rotation between the rotating elements can be reduced.

(2) In the example shown in FIG. 1, the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2 are single pinion planetary gear mechanisms, and the third engagement element CL is connected to the second sun gear S2 and the second planetary gear mechanism PG2. Connect to carrier C2.

Furthermore, when the third engagement element CL is engaged, in addition to achieving a gear ratio of 1, the input element IN and output element OUT are connected, so the power transmission path from the input element IN to the output element OUT is minimized. Therefore, power transmission loss can be further reduced.

(3) In the example shown in FIG. 1, the first planetary gear mechanism PG1 is disposed on one axial side of the second planetary gear mechanism PG2, and the third planetary gear mechanism PG1 is disposed on the other axial side of the second planetary gear mechanism PG2. A matching element CL is placed.

According to this configuration, the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2 are arranged close to each other. This increases the degree of freedom in layout of other elements, and also allows the axial dimension of the unit 100 to be reduced.

(4) Furthermore, in the example shown in FIG. 4A, the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2 are single pinion planetary gear mechanisms, and the third engagement element CL is connected to the first sun gear S1 and the second planetary gear mechanism. Connect with sun gear S2.

This arrangement is suitable for a layout design in which the third engagement element CL is not arranged between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2. If the third engagement element CL is not arranged between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2, the degree of freedom in selecting the actuator that drives the third engagement element CL can be increased. I can do it.

Furthermore, since the first to third engagement elements B1, B2, and CL can be arranged in one place, the distance between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2 can be reduced, etc. , the layout design of the first and second planetary gear mechanisms PG1 and PG2 becomes advantageous.

Furthermore, by narrowing the distance between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2, a margin is created around them, and they are arranged together in the first to third engagement elements B1, B2, and CL. It will also be easier to secure space for

(5) In the example shown in FIG. 4A, the second planetary gear mechanism PG2 is disposed on one axial side of the first planetary gear mechanism PG1, and the third planetary gear mechanism PG2 is disposed on the other axial side of the first planetary gear mechanism PG1. A matching element CL is placed.

According to this configuration, since the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2 are arranged close to each other, the degree of freedom in layout of other elements is increased, and the axial dimension of the unit 100 can be reduced. I can do it.

(6) Furthermore, in the example shown in FIGS. 1 and 4A to 4C, the third engagement element CL has a portion that overlaps with the first planetary gear mechanism PG1 when viewed in the axial direction. Further, when viewed in the axial direction, the third engagement element CL has a portion that overlaps with the second planetary gear mechanism PG2.

This allows the radial dimension of the unit 100 to be reduced.

(7) Furthermore, in the examples shown in FIGS. 4A to 4C, one side (drum 14) of the third engagement element CL is connected to one side of the first engagement element B1 or one side of the second engagement element B2. Connected.

According to this configuration, one side of the third engagement element CL and one side of the first engagement element B1 or one side of the second engagement element B2 can be made into a common part (integral part). Therefore, the number of parts of the unit 100 can be reduced.

Although the embodiments of the present invention have been described above, the above embodiments are merely application examples of the present invention, and are not intended to limit the technical scope of the present invention to the specific configurations of the above embodiments.

For example, the skeleton diagrams shown in FIGS. 1 and 4A to 4C are part of the application examples of the present invention, and the skeleton diagrams of units to which the present invention is applied are not limited to these.

Furthermore, although the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2 are each a single pinion planetary gear mechanism, they may be double pinion planetary gear mechanisms.

1: Housing 100: Unit B1: First engaging element B2: Second engaging element CL: Third engaging element S1: First sun gear (first rotating element)
C1: First carrier (second rotating element)
R1: First ring gear (third rotating element)
S2: 2nd sun gear (4th rotating element)
C2: Second carrier (fifth rotating element)
R2: 2nd ring gear (6th rotating element)
IN: Input element OUT: Output element PG1: First planetary gear mechanism PG2: Second planetary gear mechanism

Claims

an input element,
output element,
a first engagement element;
a second engagement element;
a third engagement element;
a first planetary gear mechanism in which a first rotating element, a second rotating element, and a third rotating element are arranged in this order on a collinear diagram;
a second planetary gear mechanism in which a fourth rotating element, a fifth rotating element, and a sixth rotating element are arranged in this order on the collinear diagram;
the input element is connected to the fourth rotating element,
the output element is connected to the third rotation element and the fifth rotation element,
One side of the first engagement element is connected to the second rotation element and the sixth rotation element,
the other side of the first engagement element is fixed;
One side of the second engagement element is connected to the first rotating element,
the other side of the second engagement element is fixed;
The third engaging element is a unit that connects two rotating elements selected from the first to sixth rotating elements that are not connected to each other.
The unit according to claim 1,
The first planetary gear mechanism and the second planetary gear mechanism are single pinion planetary gear mechanisms,
A unit in which the third engagement element connects the fourth rotation element and the fifth rotation element.
The unit according to claim 2,
The first planetary gear mechanism is arranged on one side of the second planetary gear mechanism in the axial direction,
A unit in which the third engagement element is disposed on the other axial side of the second planetary gear mechanism.
The unit according to claim 1,
The first planetary gear mechanism and the second planetary gear mechanism are single pinion planetary gear mechanisms,
The third engagement element is a unit that connects the first rotation element and the fourth rotation element.
The unit according to claim 4,
The second planetary gear mechanism is disposed on one side in the axial direction of the first planetary gear mechanism,
A unit in which the third engagement element is disposed on the other axial side of the first planetary gear mechanism.
The unit according to claim 3 or claim 5,
When viewed in the axial direction, the third engagement element has a portion that overlaps with the first planetary gear mechanism,
A unit in which the third engagement element has a portion that overlaps with the second planetary gear mechanism when viewed in the axial direction.
The unit according to claim 1,
One side of the third engagement element is connected to one side of the first engagement element or one side of the second engagement element.