JP5850755B2 - Power transmission mechanism - Google Patents

Description

  The present invention relates to a power transmission mechanism, and more particularly, to a power transmission mechanism including a speed change mechanism having two planetary gear mechanisms.

  As shown in FIG. 13, in Patent Document 1, the rotation shaft 248 of the motor and the drive shaft 232 a are connected and released, and the power of the motor rotation shaft 248 is decelerated in two stages to reduce the drive shaft 232 a. A transmission 260 configured to be able to transmit to is described.

  The transmission 260 includes a double-pinion planetary gear mechanism 260a, a single-pinion planetary gear mechanism 260b arranged side by side in the rotational axis direction with respect to the planetary gear mechanism 260a, and two brakes 200B1 and 200B2. Has been.

  The planetary gear mechanism 260a of a double pinion includes an external gear sun gear 261, an internal gear ring gear 262 arranged concentrically with the sun gear 261, a plurality of first pinion gears 263a meshing with the sun gear 261, and a first pinion gear 263a. A plurality of second pinion gears 263b that mesh with the pinion gear 263a and mesh with the ring gear 262; and a carrier 264 that holds the plurality of first pinion gears 263a and the plurality of second pinion gears 263b in a freely rotating and revolving manner. Yes. The sun gear 261 can be freely rotated or stopped by turning on / off the brake 200B1, and the ring gear 262 can be freely rotated or stopped by turning on / off the brake 200B2.

  The planetary gear mechanism 260b of a single pinion includes an external gear sun gear 265, an internal gear ring gear 266 arranged concentrically with the sun gear 265, and a plurality of pinion gears 267 that mesh with the sun gear 265 and mesh with the ring gear 266. And a carrier 268 that holds the plurality of pinion gears 267 so as to rotate and revolve. The sun gear 265 is connected to the rotation shaft 248 of the motor, the carrier 268 is connected to the drive shaft 232a, and the rotation of the ring gear 266 can be freely or stopped by turning on and off the brake 200B2.

  The double pinion planetary gear mechanism 260a and the single pinion planetary gear mechanism 260b are connected by a ring gear 262 and a ring gear 266, and a carrier 264 and a carrier 268, respectively. The transmission 260 can disconnect the motor rotation shaft 248 from the drive shaft 232a by turning off both the brakes 200B1 and 200B2. The transmission 260 turns off the brake 200B1 and turns on the brake 200B2 to rotate the rotation shaft 248 of the motor. Is reduced and transmitted to the drive shaft 232a, the brake 200B1 is turned on, the brake 200B2 is turned off, and the rotation of the motor rotation shaft 248 is reduced at a relatively small reduction ratio to the drive shaft 232a. introduce. When the brakes 200B1 and 200B2 are both turned on, the rotation of the rotary shaft 248 and the drive shaft 232a is prohibited.

JP 2006-234063 A

  As described above, in the transmission 260 described in Patent Document 1, the gear ratio is changed by the two planetary gear mechanisms 260a and 260b by switching the elements (sun gear 261 and ring gear 266) that restrict the rotation. However, two switching means (brakes 200B1 and 200B2) need to be provided in order to switch the elements that restrict the rotation, which may increase the number of parts and increase the size of the transmission.

  The present invention has been made in view of the above problems, and provides a power transmission mechanism that can be miniaturized.

In order to achieve the above object, the invention described in claim 1
A drive source (for example, a motor MOT in an embodiment described later);
Driven devices driven by the drive source (for example, wheels LW and RW in the embodiments described later);
A speed change mechanism (for example, speed change mechanism 3 in an embodiment described later) that is driven by the drive source and transmits power with a change in speed change ratio between the drive source and the driven device;
With
The speed change mechanism includes first and second planetary gear mechanisms (for example, first and second cycloid speed reducers 10A and 10B and first and second planetary gear speed reducers 110A and 110B in the embodiments described later). ,
The first planetary gear mechanism is
A first rotating element (for example, an outer pin 20A, an eccentric body 50A, a ring gear 120A, a sun gear 150A in an embodiment described later) and a second rotating element (for example, a curved plate 30A in an embodiment described later) that perform differential rotation with each other. Planetary gear 130A), a third rotating element (for example, inner pin 40A and planetary carrier 140A in an embodiment described later), and a fourth rotating element (for example, eccentric body 50A, outer pin 20A, sun gear 150A in an embodiment described later), Ring gear 120A),
Have
The third rotating element supports the second rotating element so as to revolve,
The second rotating element is in contact with the first rotating element and the fourth rotating element;
The second planetary gear mechanism is
A fifth rotating element (for example, an outer pin 20B, an eccentric body 50B, a ring gear 120B, and a sun gear 150B in the embodiment described later) that performs differential rotation with each other, and a sixth rotating element, for example, a curved plate 30B and a planetary gear in the embodiment described later. 130B), a seventh rotating element (for example, an inner pin 40B and a planetary carrier 140B in an embodiment described later), and an eighth rotating element (for example, an eccentric body 50B, an outer pin 20B, a sun gear 150B, and a ring gear in an embodiment described later). 120B)
Have
The seventh rotating element supports the sixth rotating element so that it can revolve,
The sixth rotation element is a power transmission mechanism (for example, a power transmission mechanism 1 of an embodiment described later) that contacts the fifth rotation element and the eighth rotation element,
The rotation axes of the first and second planetary gear mechanisms are arranged on the same line,
The third and seventh rotating elements are connected to each other;
The driven device is connected to the third and seventh rotating elements;
The first and fifth rotating elements are disposed so as to be restricted from rotating about the rotation axis,
One end side is connected to the drive source, and the other end side is provided with a power transmission shaft (for example, a power transmission shaft 5 in an embodiment described later) connected to the fourth or eighth rotation element in a switchable manner,
The power transmission shaft is connected to the drive source so as to be capable of relative movement in the rotational axis direction and to transmit power in the rotational direction.
In a power transmission shaft control device that controls the power transmission shaft (for example, an actuator ACT in an embodiment described later), the power transmission shaft is connected to the fourth rotating element at a first position, and the power transmission shaft Is controlled to be connected to the eighth rotation element at the second position.

The invention described in claim 2
A drive source (for example, a motor MOT in an embodiment described later);
Driven devices driven by the drive source (for example, wheels LW and RW in the embodiments described later);
A speed change mechanism (for example, speed change mechanism 3 in an embodiment described later) that is driven by the drive source and transmits power with a change in speed change ratio between the drive source and the driven device;
With
The speed change mechanism includes first and second planetary gear mechanisms (for example, first and second cycloid speed reducers 10A and 10B and first and second planetary gear speed reducers 110A and 110B in the embodiments described later). ,
The first planetary gear mechanism is
A first rotating element (for example, an outer pin 20A, an eccentric body 50A, a ring gear 120A, a sun gear 150A in an embodiment described later) and a second rotating element (for example, a curved plate 30A in an embodiment described later) that perform differential rotation with each other. Planetary gear 130A), a third rotating element (for example, inner pin 40A and planetary carrier 140A in an embodiment described later), and a fourth rotating element (for example, eccentric body 50A, outer pin 20A, sun gear 150A in an embodiment described later), Ring gear 120A),
Have
The third rotating element supports the second rotating element so as to revolve,
The second rotating element is in contact with the first rotating element and the fourth rotating element;
The second planetary gear mechanism is
A fifth rotating element (for example, an outer pin 20B, an eccentric body 50B, a ring gear 120B, and a sun gear 150B in the embodiment described later) that performs differential rotation with each other, and a sixth rotating element, for example, a curved plate 30B and a planetary gear in the embodiment described later. 130B), a seventh rotating element (for example, an inner pin 40B and a planetary carrier 140B in an embodiment described later), and an eighth rotating element (for example, an eccentric body 50B, an outer pin 20B, a sun gear 150B, and a ring gear in an embodiment described later). 120B)
Have
The seventh rotating element supports the sixth rotating element so that it can revolve,
The sixth rotation element is a power transmission mechanism (for example, a power transmission mechanism 1 of an embodiment described later) that contacts the fifth rotation element and the eighth rotation element,
The rotation axes of the first and second planetary gear mechanisms are arranged on the same line,
The third and seventh rotating elements are connected to each other;
The driven device is connected to the third and seventh rotating elements;
The first and fifth rotating elements are disposed so as to be restricted from rotating about the rotation axis,
One end side is connected to the drive source, and the other end side is provided with a power transmission shaft (for example, a power transmission shaft 5 in an embodiment described later) connected to the fourth or eighth rotation element in a switchable manner,
The power transmission shaft has a power transmission portion (for example, power transmission portions 7, 7A, 7B in the embodiments described later) extending in a radial direction from the power transmission shaft,
The power transmission unit is disposed between the fourth rotation element and the eighth rotation element in the rotation axis direction,
In a power transmission shaft control device that controls the power transmission shaft (for example, an actuator ACT in an embodiment described later), the power transmission shaft is in a first position, and the power transmission unit and the fourth rotation element are connected. The power transmission shaft is controlled to be connected at the second position so that the power transmission unit and the eighth rotating element are connected.

In addition to the structure of Claim 2, the invention of Claim 3 is
The first rotating element (for example, the outer pin 20A and the ring gear 120A in the embodiment described later) is disposed on the radially outer side of the second rotating element,
The fourth rotating element (for example, an eccentric body 50A and a sun gear 150A in an embodiment described later) is disposed on the radially inner side of the second rotating element,
The fifth rotating element (for example, the outer pin 20B and the ring gear 120B in the embodiment described later) is disposed on the radially outer side of the sixth rotating element,
The eighth rotating element (for example, an eccentric body 50B and a sun gear 150B in the embodiment described later) is disposed on the radially inner side of the sixth rotating element,
The third and seventh rotating elements are connected by a connecting member (for example, a connecting member 46 in an embodiment described later) extending in the rotation axis direction,
The power transmission unit is disposed on a radially inner side of the connecting member.

In addition to the structure of Claim 3, the invention of Claim 4 is
The drive source is offset from the connecting member in the direction of the rotation axis, and is disposed outside the connecting member;
At least one of the fourth rotating element and the eighth rotating element has a hollow structure having a hollow portion (for example, hollow portions 56A and 56B in the embodiments described later) in the axial center,
The power transmission shaft is inserted through the hollow portion.

In addition to the structure of any one of Claims 1-4, the invention of Claim 5 is
The reduction ratio between the fourth rotation element and the third rotation element of the first planetary gear mechanism is the reduction ratio between the eighth rotation element and the seventh rotation element of the second planetary gear mechanism. Set higher than
The power transmission shaft control device controls the power transmission shaft to the first position in a region where the rotational speed of the driven device is relatively low, and a region where the rotational speed of the driven device is relatively high Then, the power transmission shaft is controlled to the second position.

In addition to the structure of any one of Claims 1-5 , the invention of Claim 6 is
The first and second planetary gear mechanisms are cycloid reducers (for example, cycloid reducers 10A and 10B according to embodiments described later),
The fourth and eighth rotating elements are eccentric bodies (for example, eccentric bodies 50A and 50B in embodiments described later) having eccentric portions (for example, eccentric sections 52A and 52B in embodiments described later),
The second and sixth rotating elements have corrugations on the outer periphery (for example, outer peripheries 31A and 31B in the embodiments described later), and through holes (for example, the inner through holes in the embodiments described later) through which the eccentric body is inserted. 32A, 32B) and other through-holes (for example, outer through-holes 34A, 34B in the embodiments described later) disposed on the radially outer side of the through-holes are formed, and the drive source rotates. It is a curved plate (for example, curved plates 30A and 30B in the embodiments described later) that performs a rotation motion around the rotation axis,
The first and fifth rotating elements are outer pins (for example, outer pins 20A and 20B in the embodiments described later) that engage with the outer periphery of the curved plate to cause the curved plate to rotate.
The third and seventh rotating elements are inner pins (for example, inner pins 40A and 40B in the embodiments described later) that are fitted into the other through holes.

The invention described in claim 7
A drive source (for example, a motor MOT in an embodiment described later);
Driven devices driven by the drive source (for example, wheels LW and RW in the embodiments described later);
A speed change mechanism (for example, speed change mechanism 3 in an embodiment described later) that is driven by the drive source and transmits power with a change in speed change ratio between the drive source and the driven device;
With
The speed change mechanism includes first and second planetary gear mechanisms (for example, first and second cycloid speed reducers 10A and 10B and first and second planetary gear speed reducers 110A and 110B in the embodiments described later). ,
The first planetary gear mechanism is
A first rotating element (for example, an outer pin 20A, an eccentric body 50A, a ring gear 120A, a sun gear 150A in an embodiment described later) and a second rotating element (for example, a curved plate 30A in an embodiment described later) that perform differential rotation with each other. Planetary gear 130A), a third rotating element (for example, inner pin 40A and planetary carrier 140A in an embodiment described later), and a fourth rotating element (for example, eccentric body 50A, outer pin 20A, sun gear 150A in an embodiment described later), Ring gear 120A),
The third rotating element supports the second rotating element so as to be capable of revolving,
The second rotating element is in contact with the first rotating element and the fourth rotating element;
The second planetary gear mechanism is
A fifth rotating element (for example, an outer pin 20B, an eccentric body 50B, a ring gear 120B, a sun gear 150B in the embodiment described later) and a sixth rotating element (for example, a curved plate 30B in the embodiment described later) that perform differential rotation with each other. A planetary gear 130B), a seventh rotating element (for example, an inner pin 40B and a planetary carrier 140B in an embodiment described later), and an eighth rotating element (for example, an eccentric body 50B, an outer pin 20B, a sun gear 150B in an embodiment described later), Ring gear 120B),
The seventh rotating element supports the sixth rotating element so as to be capable of revolving,
The sixth rotation element is a power transmission mechanism (for example, a power transmission mechanism 1 of an embodiment described later) that contacts the fifth rotation element and the eighth rotation element,
The rotation axes of the first and second planetary gear mechanisms are arranged on the same line,
The third and seventh rotating elements are connected to each other;
The driven device is connected to the third and seventh rotating elements;
The first and fifth rotating elements are disposed so as to be restricted from rotating about the rotation axis,
One end side is connected to the drive source, and the other end side is provided with a power transmission shaft (for example, a power transmission shaft 5 in an embodiment described later) connected to the fourth or eighth rotation element in a switchable manner,
One-way rotational power transmission means that transmits forward rotational power of the power transmission shaft and does not transmit reverse rotational power between the power transmission shaft and the fourth rotational element (for example, an embodiment described later) Of the one-way clutch OWC)
The reduction ratio of the first planetary gear mechanism is set higher than the reduction ratio of the second planetary gear mechanism,
In a power transmission shaft control device that controls the power transmission shaft (for example, an actuator ACT in an embodiment described later), the power transmission shaft is disconnected from the eighth rotation element at a first position, and the power transmission is performed. Control is performed such that the shaft is connected to the eighth rotating element at the second position.

  According to the first aspect of the present invention, the rotation axes of the first and second planetary gear mechanisms are arranged on the same line, the third and seventh rotation elements are connected to each other, and the driven device is the third and Connected to 7 rotation elements, the 1st and 5th rotation elements are arranged with the rotation around the rotation axis restricted, the one end side is connected to the drive source, and the other end side can be switched to the 4th or 8th rotation element A power transmission shaft connected to the Further, in the power transmission shaft control device that controls the power transmission shaft, the power transmission shaft is connected to the fourth rotation element at the first position, and the power transmission shaft is connected to the eighth rotation element at the second position. To be controlled. In other words, the elements (fourth or eighth rotating element) connected to the drive source are configured to be switchable by controlling the power transmission shaft as the switching means by the power transmission shaft control device. Therefore, in the present invention, only one power transmission shaft as the switching means is required, and there is no need to provide two switching means as in the conventional patent document 1, the number of parts can be reduced, and the power transmission mechanism can be reduced in size. Can be

According to the second aspect of the present invention, the rotation axes of the first and second planetary gear mechanisms are arranged on the same line, the third and seventh rotation elements are connected to each other, and the driven device is the third and third planetary gear mechanisms. Connected to 7 rotation elements, the 1st and 5th rotation elements are arranged with the rotation around the rotation axis restricted, the one end side is connected to the drive source, and the other end side can be switched to the 4th or 8th rotation element A power transmission shaft connected to the Further, in the power transmission shaft control device that controls the power transmission shaft, the power transmission shaft is connected to the fourth rotation element at the first position, and the power transmission shaft is connected to the eighth rotation element at the second position. To be controlled. In other words, the elements (fourth or eighth rotating element) connected to the drive source are configured to be switchable by controlling the power transmission shaft as the switching means by the power transmission shaft control device. Therefore, in the present invention, only one power transmission shaft as the switching means is required, and there is no need to provide two switching means as in the conventional patent document 1, the number of parts can be reduced, and the power transmission mechanism can be reduced in size. Can be
Moreover, since the power transmission part which transmits power with the 4th and 8th rotation element is arrange | positioned between a 4th rotation element and an 8th rotation element in the rotating shaft direction, there is only one said power transmission part. The power transmission mechanism can be prevented from expanding in the direction of the rotational axis.

According to the third aspect of the present invention, the power transmission portion is disposed on the radially inner side of the connecting member that extends in the rotational axis direction and connects the third and seventh rotating elements. Compared with the case where it arrange | positions to, it becomes possible to prevent the expansion to the radial direction of a power transmission mechanism.
In addition, the first and fifth rotating elements arranged to be restricted from rotating around the rotation axis are arranged on the radially outer side of the second and sixth rotating elements, and are connected to the power transmission shaft in a switchable manner. And the eighth rotating element is disposed radially inward of the second and sixth rotating elements, so that the first and fifth rotating elements are disposed radially inward of the second and sixth rotating elements, Compared with the case where the eighth rotating element is arranged on the radially outer side of the second and sixth rotating elements, it is possible to prevent the power transmission mechanism from expanding in the radial direction.

According to the fourth aspect of the present invention, the drive source is offset from the connecting member in the rotational axis direction and is disposed outside the connecting member, so that it is possible to prevent the connecting member from expanding in the rotational axis direction. The size of the drive source in the radial direction can be enlarged.
In addition, since the power transmission shaft is inserted into the hollow portion provided at the center of at least one of the fourth rotation element and the eighth rotation element, it is possible to prevent the power transmission mechanism from expanding in the radial direction.

  According to the invention described in claim 5, in the region where the rotational speed of the driven device is relatively low, the position of the power transmission shaft is controlled to the first position, and the reduction ratio is higher than that of the second planetary gear mechanism. In the region where the power of the drive source is transmitted to the first planetary gear mechanism and the rotational speed of the driven device is relatively high, the position of the power transmission shaft is controlled to the second position, and the speed is reduced more than the first planetary gear mechanism. Since the power of the drive source is transmitted to the second planetary gear mechanism having a low ratio, it is possible to deal with a wide range of rotation.

According to the sixth aspect of the present invention, since the first and second planetary gear mechanisms are composed of cycloid reduction gears, the gear ratio is higher than when the first and second planetary gear mechanisms are planetary gear type reduction gears. The power transmission mechanism can be prevented from expanding in the radial direction.

According to the seventh aspect of the present invention, the element (fourth or eighth rotating element) connected to the drive source via the power transmission shaft can be switched by controlling the power transmission shaft as the switching means. It is configured. Therefore, in the present invention, only one power transmission shaft as the switching means is required, and there is no need to provide two switching means as in the conventional patent document 1, the number of parts can be reduced, and the power transmission mechanism can be reduced in size. Can be
Furthermore, since the speed change mechanism has first and second planetary gear mechanisms with different reduction ratios, two-stage speed change is possible by switching the mechanism connected to the drive source.
Further, the unidirectional rotational power transmission means that transmits the rotational power in the forward direction of the power transmission shaft and does not transmit the rotational power in the reverse direction has a reduction ratio that is higher than that of the power transmission shaft and the second planetary gear mechanism. And the fourth rotating element of the planetary gear mechanism. Therefore, when the connection is switched from the first planetary gear mechanism on the low speed stage side to the second planetary gear mechanism on the high speed stage side, there is no neutral state, and smooth shifting is possible.
Further, even when the power transmission shaft is not connected to the fourth and eighth rotating elements, the power of the drive source can be transmitted to the first planetary gear mechanism via the one-way rotational power transmission means.

It is a skeleton figure which shows the power transmission mechanism which concerns on 1st Embodiment of this invention, and is the figure which showed the cycloid reduction gear shown in FIG. 2 in the AA 'cross section. It is sectional drawing of the cycloid reduction gear of 1st Embodiment. It is a skeleton figure which shows the state which the power transmission part of the power transmission shaft connected to the 1st cycloid reduction gear. It is a skeleton figure which shows the state which the power transmission part of the power transmission shaft connected to the 2nd cycloid reduction gear. It is a skeleton figure which shows the power transmission mechanism which concerns on the modification 1 of 1st Embodiment. It is a skeleton figure which shows the power transmission mechanism which concerns on the modification 2 of 1st Embodiment. It is a skeleton figure which shows the power transmission mechanism which concerns on the modification 3 of 1st Embodiment. It is a skeleton figure which shows the power transmission mechanism which concerns on the modification 4 of 1st Embodiment. It is a skeleton figure which shows the power transmission mechanism which concerns on 2nd Embodiment of this invention. It is a skeleton figure which shows the state which the power transmission part of the power transmission shaft connected to the 1st cycloid reduction gear. It is a skeleton figure which shows the state which the power transmission part of the power transmission shaft connected to the 2nd cycloid reduction gear. It is a skeleton figure which shows the power transmission mechanism which concerns on 3rd Embodiment of this invention. It is a skeleton figure which shows the conventional transmission.

  Hereinafter, embodiments of a power transmission mechanism according to the present invention will be described in detail with reference to the drawings.

(First embodiment)
As shown in FIG. 1, a power transmission mechanism 1 according to the present embodiment is provided in a vehicle such as an automobile, for example, and includes a motor MOT as a drive source and left and right wheels LW as driven devices driven by the motor MOT. And a transmission mechanism 3 that is driven by the motor MOT and transmits power between the motor MOT and the wheels LW and RW with a change in transmission ratio.

  The speed change mechanism 3 includes first and second cycloid reduction gears 10A and 10B as first and second planetary gear mechanisms arranged side by side so that their rotation axes are on the same line, and one end side in the direction of the rotation axis (see FIG. 1, the left side) is connected to the motor MOT, and the other end side (right side in FIG. 1) is connected to the first or second cycloid reducer 10 </ b> A, 10 </ b> B in a switchable manner, , A differential gear DIFF that is connected to the second cycloid reducers 10A and 10B so as to be able to transmit power and distributes the power to the left and right drive shafts LD and RD for transmission.

  Referring also to FIG. 2, the first and second cycloid reducers 10A and 10B include outer pins 20A and 20B as first and fifth rotating elements that perform differential rotation with each other, and a second that is disposed radially inward. , Curved plates 30A and 30B as sixth rotating elements, inner pins 40A and 40B as third and seventh rotating elements, and fourth and eighth rotating elements disposed radially inward of the curved plates 30A and 30B. As eccentric bodies 50A and 50B. The inner pins 40A and 40B are disposed radially inward of the outer pins 20A and 20B and radially outward of the eccentric bodies 50A and 50B, and support the curved plates 30A and 30B so that they can revolve. Further, the curved plates 30A and 30B are in contact with the outer pins 20A and 20B and the eccentric bodies 50A and 50B.

  The eccentric bodies 50A and 50B are formed integrally with the rotation shaft portions 51A and 51B extending in the rotation axis direction and the rotation shaft direction intermediate portions of the rotation shaft portions 51A and 51B, and the shaft centers of the rotation shaft portions 51A and 51B. The eccentric parts 52A and 52B are eccentric by an eccentric amount e, and the hollow structure has hollow parts 56A and 56B through which the power transmission shaft 5 can be inserted. Inner ends in the rotation axis direction of the rotation shaft portions 51A and 51B can be connected to a power transmission portion 7 (described later) of the power transmission shaft 5, and the rotation shaft portions 51A and 51B rotate by the driving force of the motor MOT. As a result, the eccentric portions 52A and 52B rotate eccentrically. Further, bearings 53A and 53B are provided on the outer peripheral portions of the eccentric portions 52A and 52B, and the plurality of rollers 54A and 54B of the bearings 53A and 53B are provided in the inner through holes 32A and 32B ( The curved plates 30A and 30B are rotatably supported. Accordingly, when the eccentric portions 52A and 52B of the eccentric bodies 50A and 50B are eccentrically rotated with the rotation of the motor MOT, the curved plates 30A and 30B are centered on the rotation axes of the first and second cycloid reducers 10A and 10B. As described above, eccentric rotation (rotation) is performed in the opposite direction to the eccentric bodies 50A and 50B.

  The curved plates 30A, 30B penetrate the shaft center from one end side surface to the other end side surface in the rotational axis direction, and the inner through holes 32A, 32B through which the eccentric bodies 50A, 50B are inserted and the radial directions of the inner through holes 32A, 32B. Outer through-holes 34A and 34B penetrating from one end side surface to the other end side surface in the rotation axis direction are formed on the outer side, and the outer peripheries 31A and 31B have a waveform composed of a trochoidal curve such as epitrochoid. A plurality of outer through holes 34A and 34B are provided at equal intervals on the circumference centered on the axis of the curved plates 30A and 30B, and the inner pins 40A and 40B are fitted therein.

  The inner pins 40A, 40B are provided at equal intervals on the circumference centering on the rotation axis of the first and second cycloid reducers 10A, 10B, and are inserted into the plurality of outer through holes 34A, 34B. 42A, 42B and a pair of substantially annular flanges 44A, 44B extending radially inward from both sides of the plurality of pins 42A, 42B in the rotational axis direction. The radially inner ends of the pair of flanges 44A and 44B are supported by the rotation shafts 51A and 51B of the eccentric bodies 50A and 50B via bearings 58A and 58B so as to be relatively rotatable. Further, since the flanges 44A and 44B on the inner side in the rotation axis direction of the first and second cycloid reducers 10A and 10B are connected to each other by a substantially annular connecting member 46 extending in the rotation axis direction, 40B revolves integrally around the rotation axis of the first and second cycloid reducers 10A and 10B. The rotational power of the inner pins 40A, 40B is transmitted to the differential gear DIFF by a final gear 48 provided at the intermediate portion in the rotational axis direction of the connecting member 46.

  The outer pins 20A and 20B are composed of a plurality of pins 24A and 24B provided at equal intervals on a pin holder (not shown) whose rotation is restricted. Therefore, the plurality of pins 24A and 24B are restricted from rotating (revolving) around the rotation axis of the first and second cycloid reducers 10A and 10B. Further, the plurality of pins 24A, 24B are engaged with the outer peripheries 31A, 31B of the curved plates 30A, 30B, and rotate around the rotation axes of the first and second cycloid reducers 10A, 10B on the curved plates 30A, 30B. Give rise to The plurality of pins 24A and 24B may be configured to rotate as long as rotation (revolution) around the rotation axis of the first and second cycloid reducers 10A and 10B is restricted.

  In FIG. 2, for the sake of simplicity, the first and second cycloid reducers 10A and 10B include the number of waves on the outer circumferences 31A and 31B of the curved plates 30A and 30B and the pins 24A and 24A of the outer pins 20A and 20B. Although the number of 24B is illustrated equally, in reality, the reduction ratio between the eccentric body 50A of the first cycloid reducer 10A and the inner pin 40A is different from the eccentric body 50B and the inner pin 40B of the second cycloid reducer. It is set to be higher than the reduction ratio during That is, the first cycloid reduction gear 10A is a reduction gear for a low speed stage, and the second cycloid reduction gear 10B is a reduction gear for a high speed stage.

  One end of the power transmission shaft 5 in the rotational axis direction is connected to the motor MOT by a slide spline, and the motor MOT and the power transmission shaft 5 are capable of relative movement in the rotational axis direction, and power in the rotational direction. Connected to allow transmission. Further, the power transmission shaft 5 extends to the other end side in the rotation axis direction and passes through the hollow portions 56A and 56B of the eccentric bodies 50A and 50B. Further, the power transmission shaft 5 is formed with a power transmission portion 7 extending radially outward from the power transmission shaft 5 between the eccentric bodies 50A and 50B in the rotational axis direction and radially inside the connecting member 46. The actuator ACT as a power transmission shaft control device is connected to the other end side in the rotational axis direction from the first and second cycloid reducers 10A and 10B.

  In the actuator ACT, displacement control of the power transmission shaft 5 in the rotational axis direction can be performed by a shift fork SF (operator). As shown in FIG. 3, the power transmission shaft 5 is displaced toward one end in the rotational axis direction. The power transmission unit 7 and the rotating shaft 51A of the eccentric body 50A are connected (the position of the power transmission shaft 5 at this time is referred to as “first position”), and the power transmission shaft as shown in FIG. 5 is displaced to the other end side in the rotation axis direction, thereby connecting the power transmission unit 7 and the rotation shaft unit 51B of the eccentric body 50B (the position of the power transmission shaft 5 at this time is “second position”). Call it.) Note that the connection structure between the power transmission shaft 5 and the eccentric bodies 50A and 50B may be synchronized or a dog clutch.

  Here, the actuator ACT controls the power transmission shaft 5 to the first position in a region where the rotational speeds of the wheels LW and RW are relatively low, and is connected to the first cycloid reducer 10A for the low speed stage. Since the LW and RW rotation speed is controlled to the second position in the relatively high region, the power transmission shaft 5 is connected to the second cycloid reducer 10B for the high speed stage, and the wheels LW and RW are driven. A wide range of rotation is possible. During regeneration, the rotational power of the wheels LW and RW can be input to the motor MOT by controlling the power transmission shaft 5 to the first and second positions. When the power transmission shaft 5 is displaced to a position other than the first and second positions (for example, the state of FIG. 1), the power of the motor MOT is not transmitted to the wheels LW and RW, and the neutral state Become.

  As described above, according to the power transmission mechanism 1 of the present embodiment, the rotation axes of the first and second cycloid reducers 10A and 10B are arranged on the same line, and the inner pins 40A and 40B are connected to each other. The wheels LW and RW are connected to the inner pins 40A and 40B, and the outer pins 20A and 20B are arranged so as to be restricted from rotating around the rotation axis, one end side is connected to the motor MOT, and the other end side is connected to the eccentric body 50A or 50B. On the other hand, a power transmission shaft 5 connected to be switchable is provided. Further, in the actuator ACT for controlling the power transmission shaft 5, the power transmission shaft 5 is connected to the eccentric body 50A at the first position, and the power transmission shaft 5 is connected to the eccentric body 50B at the second position. To control. That is, the elements (eccentric bodies 50A, 50B) connected to the motor MOT are configured to be switchable by controlling the power transmission shaft 5 as switching means by the actuator ACT. Therefore, in the present invention, only one power transmission shaft 5 as the switching means is required, and there is no need to provide two switching means as in the conventional patent document 1, the number of parts can be reduced, and the power transmission mechanism 1 Can be miniaturized.

  In addition, since the power transmission unit 7 that transmits power to the eccentric bodies 50A and 50B is disposed between the eccentric bodies 50A and 50B in the rotation axis direction, the power transmission unit 7 can be configured with only one power source. It becomes possible to prevent the transmission mechanism 1 from expanding in the direction of the rotation axis.

Moreover, since the power transmission part 7 is arrange | positioned in the radial direction inner side of the connection member 46 which extends in a rotating shaft direction and connects inner pin 40A, 40B, compared with the case where it arrange | positions at the radial direction outer side of the connection member 46. Thus, it is possible to prevent the power transmission mechanism 1 from expanding in the radial direction.
In addition, the first and fifth rotating elements (outer pins 20A, 20B), which are arranged so as to be restricted from rotating around the rotation axis, are arranged on the radially outer side of the second and sixth rotating elements (curved plates 30A, 30B). Since the fourth and eighth rotating elements (eccentric bodies 50A, 50B) connected to the power transmission shaft 5 are arranged radially inside the second and sixth rotating elements (curved plates 30A, 30B), When the first and fifth rotating elements are disposed radially inside the second and sixth rotating elements, and the fourth and eighth rotating elements are disposed radially outside the second and sixth rotating elements (ie, When the first and fifth rotating elements are the eccentric bodies 50A and 50B and the second and sixth rotating elements are the outer pins 20A and 20B: the radial direction of the power transmission mechanism 1 as compared with the modified example 4) described later It is possible to prevent the expansion to.

Further, since the motor MOT is offset from the connecting member 46 in the rotational axis direction and is disposed outside the connecting member 46, it is possible to prevent the connecting member 46 from being expanded in the rotational axis direction, and the radial direction of the motor MOT. The size of can be expanded.
Further, since the power transmission shaft 5 is inserted into the hollow portion 56 provided in the shaft centers of the eccentric bodies 50A and 50B, it is possible to prevent the power transmission mechanism 1 from expanding in the radial direction.

  Further, in the region where the rotational speeds of the wheels LW and RW are relatively low, the position of the power transmission shaft 5 is controlled to the first position, and the first cycloid reducer 10A having a higher reduction ratio than the second cycloid reducer 10B. In the region where the power of the motor MOT is transmitted and the rotation speed of the wheels LW and RW is relatively high, the position of the power transmission shaft 5 is controlled to the second position, and the reduction ratio is higher than that of the first cycloid reducer 10A. Since the power of the motor MOT is transmitted to the low second cycloid reduction gear 10B, it is possible to deal with a wide rotation range.

  Further, the motor MOT and one end side of the power transmission shaft 5 are connected by a slide spline so as to be capable of relative movement in the rotational axis direction and to transmit power in the rotational direction. In other words, the motor MOT that supplies power is fixed, and the power transmission shaft 5 that transmits power from the motor MOT is arranged so as to be movable in the direction of the rotation axis. The mechanism 1 can be downsized.

  In addition, since the first and second planetary gear mechanisms of the present embodiment are constituted by cycloid reducers, the gear ratio can be made larger than when the first and second planetary gear mechanisms are planetary gear type reducers. It is possible to suppress the expansion of the power transmission mechanism 1 in the radial direction.

(Modification 1)
In the power transmission mechanism 1 according to the first embodiment described above, the power transmission shaft 5 is connected to the power transmission shaft 5 at the other end side in the rotational axis direction from the first and second cycloid reducers 10A and 10B, that is, at the distal side of the motor MOT. The actuator ACT is assumed to be connected. However, as shown in FIG. 5, the actuator ACT is connected to the power transmission shaft 5 at one end side in the rotational axis direction from the first and second cycloid reducers 10A and 10B, that is, at the proximal side of the motor MOT. It is good also as a structure. When configured in this manner, the other end portion in the rotation axis direction of the power transmission shaft 5 extending through the hollow portion 56A of the eccentric body 50A and extending to the other end side in the rotation axis direction is between the eccentric bodies 50A and 50B in the rotation axis direction. And a power transmission portion 7 extending outward in the radial direction is formed at the other end in the rotational axis direction. Accordingly, there is no need to provide the hollow portion 56B in the eccentric body 50B of the second cycloid reduction gear 10B, the eccentric body 50B has a solid structure, and the length of the power transmission shaft 5 in the rotation axis direction can be shortened. Therefore, expansion of the power transmission mechanism 1 can be further suppressed.

(Modification 2)
As shown in FIG. 6, the power transmission unit 7 formed on the power transmission shaft 5 includes first and second power transmission units 7 </ b> A and 7 </ b> B formed on the outer sides in the rotation axis direction of the eccentric bodies 50 </ b> A and 50 </ b> B, respectively. It is good also as composition which becomes. In this case, the actuator ACT displaces the power transmission shaft 5 to the other end side in the rotation axis direction to the first position, so that the first power transmission portion 7A and the rotation shaft portion 51A of the eccentric body 50A. Are connected, and the power transmission shaft 5 is displaced to one end side in the rotational axis direction to be in the second position, thereby bringing the second power transmission portion 7B and the rotational shaft portion 51B of the eccentric body 50B into a connected state. .

(Modification 3)
Further, as shown in FIG. 7, in the power transmission mechanism 1 of the second modification, the power transmission shaft 5 is closer to one end side in the rotation axis direction than the first and second cycloid reducers 10A and 10B, that is, near the motor MOT. The actuator ACT may be connected on the rear side.

(Modification 4)
Further, as shown in FIG. 8, the first and fifth rotating elements arranged with the rotation around the rotation axis being restricted are the eccentric bodies 50A and 50B, and are connected to the power transmission shaft 5 in a switchable manner. The eighth rotation element may be the outer pins 20A and 20B.

  In this case, the eccentric bodies 50A and 50B are connected to each other in the rotation axis direction to constitute one eccentric body having a solid structure. The eccentric bodies 50A and 50B may be formed separately as in the first embodiment as long as the rotation around the rotation axis is restricted.

  In addition, the power transmission shaft 5 is disposed radially outside the outer pins 20 </ b> A and 20 </ b> B, and first and second power transmission parts 7 </ b> A and 7 </ b> B that constitute the power transmission part 7 are formed. The actuator ACT displaces the power transmission shaft 5 toward one end in the rotational axis direction to be in the first position, whereby the first power transmission portion 7A and the outer pin 20A are connected, and the power transmission shaft 5 is turned into the rotational axis. The second power transmission unit 7B and the outer pin 20B are brought into a connected state by being displaced to the other end side in the direction to be the second position.

  By configuring as described above, the power of the motor MOT can be transmitted to the outer pins 20A and 20B in a switchable manner, and the outer pins 20A and 20B to which the power has been transmitted are the first and second cycloid reducers 10A and 10B. , And the driving force is output to the wheels LW and RW via the curved plates 30A and 30B, the inner pins 40A and 40B, the connecting member 46, and the like.

(Second Embodiment)
Next, a power transmission mechanism according to a second embodiment of the present invention will be described. The power transmission mechanism of the present embodiment has the same basic configuration as that of the power transmission mechanism of the first embodiment. Therefore, the same reference numerals are assigned to the same parts to omit or simplify the description, with the focus on the different parts. explain.

  As shown in FIG. 9, the forward direction of the power transmission shaft 5 driven by the motor MOT is between the power transmission shaft 5 and the rotary shaft portion 51A of the eccentric body 50A of the low-speed first cycloid reduction gear 10A. A one-way clutch OWC is arranged as a one-way rotational power transmission means that transmits rotational power to the eccentric body 50A and does not transmit reverse rotational power.

  When the one-way clutch OWC is arranged in this way, the actuator ACT does not connect the power transmission portion 7 of the power transmission shaft 5 to the rotation shaft portion 51B of the eccentric body 50B (the position of the power transmission shaft 5 at this time is “first position”). In this case, the rotational power of the power transmission shaft 5 is input to the first cycloid reducer 10A in the low speed stage. More specifically, the non-connected state of the power transmission shaft 5 and the eccentric body 50B at the first position means that the power transmission portion 7 of the power transmission shaft 5 rotates the eccentric bodies 50A and 50B as shown in FIG. The state where it is not connected to either of the shaft portions 51A and 51B, or the state where the power transmission portion 7 of the power transmission shaft 5 is connected to the rotating shaft portion 51A of the eccentric body 50A as shown in FIG. In the state shown in FIG. 9, the rotational power of the power transmission shaft 5 is input to the rotational shaft portion 51A of the eccentric body 50A via the one-way clutch OWC, and in the state shown in FIG. 10, the power transmission of the power transmission shaft 5 is performed. It is input to the rotating shaft 51 </ b> A of the eccentric body 50 </ b> A via the part 7.

  11, the position where the actuator ACT connects the power transmission portion 7 of the power transmission shaft 5 to the rotation shaft portion 51B of the eccentric body 50B (the position of the power transmission shaft 5 at this time is referred to as “second position”). In this case, the rotational power of the power transmission shaft 5 is input to the second cycloid reducer 10B at the high speed stage.

  Here, the actuator ACT controls the power transmission shaft 5 to the first position in a region where the rotational speeds of the wheels LW and RW are relatively low, and is connected to the first cycloid reducer 10A for the low speed stage. Since the LW and RW rotation speed is controlled to the second position in a relatively high region, the power transmission shaft 5 is connected to the second cycloid reducer 10B for the high speed stage, and the wheels LW and RW are driven. It becomes possible to correspond to the rotation range. In particular, in this embodiment, when the connection of the power transmission shaft 5 is switched from the first cycloid reduction gear 10A for the low speed stage to the second cycloid reduction gear 10B for the high speed stage, the power transmission is not performed. Since the one-way clutch OWC is disengaged at the moment when the power transmission portion 7 of the shaft 5 is connected to the rotating shaft portion 51B of the eccentric body 50B, seamless (no idle time) switching is possible. Further, when the connection of the power transmission shaft 5 is switched from the high speed second cycloid reducer 10B to the low speed first cycloid reducer 10A, the power transmission shaft 5 may be controlled to the first position again. In this case, the power transmission unit 7 of the power transmission shaft 5 is more eccentric than the state in which the power transmission unit 7 of the power transmission shaft 5 is connected to the rotary shaft 51A of the eccentric body 50A (see FIG. 10). It is desirable to control so that it is not connected to either of the rotating shaft portions 51A and 51B (see FIG. 9).

  Further, at the time of regeneration, the power transmission unit 7 of the power transmission shaft 5 is controlled so as to be connected to the rotation shaft portions 51A and 51B of the eccentric bodies 50A and 50B (see FIGS. 10 and 11), thereby the wheels LW and RW are controlled. Rotational power can be input to the motor MOT. In particular, in the case of this embodiment, the amount of regeneration can be increased by connecting the power transmission shaft 5 and the eccentric body 50A by a dog clutch. When regeneration is not required and the motor MOT is stopped when the wheels LW and RW are rotating, the power transmission unit 7 of the power transmission shaft 5 is connected to the rotation shafts 51A and 51B of the eccentric bodies 50A and 50B. What is necessary is just to set it as the state (refer FIG. 9) which is not connected to either.

As described above, according to the power transmission mechanism 1 of the present embodiment, the elements (eccentric bodies 50A, 50B) connected to the motor MOT via the power transmission shaft 5 are the power transmission shaft 5 as switching means. By being controlled, it can be switched. Therefore, in the present invention, only one power transmission shaft 5 as the switching means is required, and there is no need to provide two switching means as in the conventional patent document 1, the number of parts can be reduced, and the power transmission mechanism 1 Can be miniaturized.
Furthermore, since the speed change mechanism 3 includes the first and second cycloid reducers 10A and 10B having different speed reduction ratios, a two-stage speed change is possible by switching the mechanism connected to the motor MOT.
Further, the one-way clutch OWC that transmits the rotational power in the forward direction of the power transmission shaft 5 and does not transmit the rotational power in the reverse direction has a first reduction ratio higher than that of the power transmission shaft 5 and the second cycloid reducer 10B. It arrange | positions between 50 A of eccentric bodies of 10 A of cycloid reduction gears. Therefore, when the connection is switched from the first cycloid reduction gear 10A on the low speed stage side to the second cycloid reduction gear 10B on the high speed stage side, a neutral state is not brought about, and a smooth speed change is possible.

  Note that, also in the power transmission mechanism 1 of the present embodiment, the first and fifth rotating elements that are disposed so as to be restricted from rotating about the rotation axis, as in Modification 4 (see FIG. 8) of the first embodiment. May be the eccentric bodies 50A and 50B, and the fourth and eighth rotating elements connected to the power transmission shaft 5 in a switchable manner may be the outer pins 20A and 20B. In this case, the one-way clutch OWC is provided between the power transmission shaft 5 and the outer pin 20A of the first low-speed first cycloid reducer 10A.

(Third embodiment)
Next, a power transmission mechanism according to a third embodiment of the present invention will be described. The power transmission mechanism of the present embodiment has the same basic configuration as the power transmission mechanism of the first embodiment and is different only in the configuration of the first and second planetary gear mechanisms. The description will be omitted or simplified by attaching, and the differences will be described in detail.

  As shown in FIG. 12, the speed change mechanism 3 of the present embodiment includes first and second planetary gear type reduction gears as first and second planetary gear mechanisms that are arranged side by side so that their rotational axes are on the same line. 110A and 110B. The first and second planetary gear type speed reducers 110A and 110B include substantially ring-shaped ring gears 120A and 120B serving as first and fifth rotating elements disposed so as to be restricted from rotating around the rotation axis, and ring gears 120A, A plurality of planetary gears 130A and 130B as second and sixth rotating elements that are arranged radially inward of 120B and mesh with the ring gears 120A and 120B, and a third and a third that support the plurality of planetary gears 130A and 130B in a revolving manner. Planetary carriers 140A and 140B as seven rotating elements, and sun gears 150A and 150B as fourth and eighth rotating elements disposed on the radial inner side of the planetary gears 130A and 130B and meshing with the planetary gears 130A and 130B.

  The planetary carriers 140A and 140B are connected to each other by the connecting member 46 and rotate together. The rotational power of the planetary carriers 140A and 140B is transmitted to the differential gear DIFF by the final gear 48 provided at the intermediate portion in the rotational axis direction of the connecting member 46. The ring gears 120A and 120B are arranged such that the rotation around the rotation axis is restricted.

  Here, the outer diameter of the sun gear 150A is smaller than the outer diameter of the sun gear 150B, and the inner diameter of the ring gear 120A is larger than the inner diameter of the ring gear 120B. That is, the number of teeth of sun gear 150A is smaller than the number of teeth of sun gear 150B, and the number of teeth of ring gear 120A is larger than the number of teeth of ring gear 120B. Therefore, the reduction ratio of the first planetary gear type reduction gear 110A is higher than the reduction ratio of the second planetary gear type reduction device, and the first and second planetary gear reduction devices 110A and 110B are for the low speed stage and the high speed, respectively. It is considered as a stage reducer.

  The actuator ACT controls the power transmission shaft 5 to the first position in a region where the rotational speeds of the wheels LW and RW are relatively low, and the power transmission shaft 5 is controlled by the first planetary gear speed reducer 110A for the low speed stage. The power transmission shaft 5 is connected to the sun gear 150A of the second planetary gear speed reducer 110B for the high speed stage by connecting to the sun gear 150A and controlling to the second position in the region where the rotational speeds of the wheels LW and RW are relatively high. Since they are connected and the wheels LW and RW are driven, a wide range of rotation can be handled. During regeneration, the rotational power of the wheels LW and RW can be input to the motor MOT by controlling the power transmission shaft 5 to the first and second positions. When the power transmission shaft 5 is displaced to a position other than the first and second positions, the power of the motor MOT is not transmitted to the wheels LW and RW, and a neutral state is obtained.

  Thus, according to the power transmission mechanism of the present embodiment, it is possible to achieve the same effects as the effects of the power transmission mechanism of the first embodiment. As described above, in order to increase the speed ratio of the speed change mechanism 3, it is desirable to configure the planetary gear mechanism with a cycloid reduction gear as in the first embodiment.

  Also in the power transmission mechanism of the present embodiment, similarly to the second embodiment, the one-way clutch OWC is a first planetary gear having a higher reduction ratio than the power transmission shaft 5 and the second planetary gear type speed reducer 110B. It may be configured to be disposed between the sun gear 150A of the type reduction gear 110A.

  Further, as in the fourth modification of the first embodiment, the first and fifth rotating elements arranged with the rotation around the rotation axis being restricted are the sun gears 150A and 150B, and are switchably connected to the power transmission shaft 5. The fourth and eighth rotating elements may be ring gears 120A and 120B.

In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.
For example, in the above-described embodiment, the wheels LW and RW are applied as the driven devices, but other rotating mechanisms such as a winch may be applied.

  The eccentric bodies 50A and 50B may have a configuration in which a plurality of eccentric portions 52A and 52B are provided with different phases in order to cancel the centrifugal force due to the eccentric motion. For example, when the eccentric bodies 50A and 50B are provided with the three eccentric portions 52A and 52B, the eccentric bodies 50A and 50B are provided with phases shifted by 120 °.

  In the above-described embodiment, the first planetary gear mechanism is arranged on one end side in the rotation axis direction and the second planetary gear mechanism is arranged on the other end side. However, the second planetary gear mechanism is arranged on one end side. The first planetary gear mechanism may be disposed on the other end side.

DESCRIPTION OF SYMBOLS 1 Power transmission mechanism 3 Transmission mechanism 5 Power transmission shaft 7, 7A, 7B Power transmission part 10A, 10B Cycloid speed reducer (planetary gear mechanism)
20A outer pin (first rotating element or fourth rotating element)
20B Outer pin (5th or 8th rotating element)
24A, 24B Pin 30A Curved plate (second rotating element)
30B Curved plate (sixth rotating element)
31A, 31B Outer perimeter 32A, 32B Inside through hole (through hole)
34A, 34B Outer through hole (through hole)
40A inner pin (third rotating element)
40B Inner pin (seventh rotating element)
42A, 42B Pins 44A, 44B Flange 46 Connecting member 48 Final gear 50A Eccentric body (fourth rotating element or first rotating element)
50B Eccentric body (8th rotating element or 5th rotating element)
51A, 51B Rotating shaft portion 52A, 52B Eccentric portion 53A, 53B Bearing 54A, 54B Roller 56A, 56B Hollow portion 58A, 58B Bearing 110A, 110B Planetary gear type reduction gear (planetary gear mechanism)
120A ring gear (first rotating element or fourth rotating element)
120B ring gear (5th or 8th rotating element)
130A planetary gear (second rotating element)
130B Planetary gear (6th rotating element)
140A planetary carrier (third rotating element)
140B planetary carrier (seventh rotating element)
150A sun gear (fourth rotating element or first rotating element)
150B sun gear (8th or 5th rotating element)
ACT Actuator (Power transmission shaft controller)
DIFF Differential gear LD, RD Drive shaft LW, RW Wheel (driven device)
MOT motor (drive source)
OWC one-way clutch (unidirectional rotational power transmission means)
SF shift fork

Claims (7)

A driving source;
A driven device driven by the drive source;
A speed change mechanism that is driven by the drive source and transmits power with a change in speed change ratio between the drive source and the driven device;
With
The speed change mechanism has first and second planetary gear mechanisms,
The first planetary gear mechanism is
A first rotating element, a second rotating element, a third rotating element, and a fourth rotating element that perform differential rotation with each other;
Have
The third rotating element supports the second rotating element so as to revolve,
The second rotating element is in contact with the first rotating element and the fourth rotating element;
The second planetary gear mechanism is
A fifth rotating element, a sixth rotating element, a seventh rotating element, and an eighth rotating element that perform differential rotation with respect to each other;
Have
The seventh rotating element supports the sixth rotating element so that it can revolve,
The sixth rotating element is a power transmission mechanism that contacts the fifth rotating element and the eighth rotating element,
The rotation axes of the first and second planetary gear mechanisms are arranged on the same line,
The third and seventh rotating elements are connected to each other;
The driven device is connected to the third and seventh rotating elements;
The first and fifth rotating elements are disposed so as to be restricted from rotating about the rotation axis,
One end side is connected to the drive source, and the other end side includes a power transmission shaft that is switchably connected to the fourth or eighth rotating element,
The power transmission shaft is connected to the drive source so as to be capable of relative movement in the rotational axis direction and to transmit power in the rotational direction.
In the power transmission shaft control device for controlling the power transmission shaft, the power transmission shaft is connected to the fourth rotation element at a first position, and the power transmission shaft is connected to the eighth rotation element at a second position. And a power transmission mechanism that is controlled so as to be in a connected state. A driving source;
A driven device driven by the drive source;
A speed change mechanism that is driven by the drive source and transmits power with a change in speed change ratio between the drive source and the driven device;
With
The speed change mechanism has first and second planetary gear mechanisms,
The first planetary gear mechanism is
A first rotating element, a second rotating element, a third rotating element, and a fourth rotating element that perform differential rotation with each other;
Have
The third rotating element supports the second rotating element so as to revolve,
The second rotating element is in contact with the first rotating element and the fourth rotating element;
The second planetary gear mechanism is
A fifth rotating element, a sixth rotating element, a seventh rotating element, and an eighth rotating element that perform differential rotation with respect to each other;
Have
The seventh rotating element supports the sixth rotating element so that it can revolve,
The sixth rotating element is a power transmission mechanism that contacts the fifth rotating element and the eighth rotating element,
The rotation axes of the first and second planetary gear mechanisms are arranged on the same line,
The third and seventh rotating elements are connected to each other;
The driven device is connected to the third and seventh rotating elements;
The first and fifth rotating elements are disposed so as to be restricted from rotating about the rotation axis,
One end side is connected to the drive source, and the other end side includes a power transmission shaft that is switchably connected to the fourth or eighth rotating element,
The power transmission shaft has a power transmission portion extending in a radial direction from the power transmission shaft,
The power transmission unit is disposed between the fourth rotation element and the eighth rotation element in the rotation axis direction,
In the power transmission shaft control device for controlling the power transmission shaft, the power transmission shaft is in the first position, the power transmission unit and the fourth rotating element are connected, and the power transmission shaft is in the second position. , characterized in that said power transmission portion and the eighth rotary element is controlled to be connected dynamic force transmission mechanism. The first rotating element is disposed radially outside the second rotating element;
The fourth rotating element is disposed radially inward of the second rotating element;
The fifth rotating element is disposed radially outside the sixth rotating element;
The eighth rotating element is disposed radially inward of the sixth rotating element;
The third and seventh rotating elements are connected by a connecting member extending in the rotation axis direction,
The power transmission mechanism according to claim 2, wherein the power transmission unit is disposed radially inward of the connecting member. The drive source is offset from the connecting member in the direction of the rotation axis, and is disposed outside the connecting member;
At least one of the fourth rotating element and the eighth rotating element has a hollow structure having a hollow portion in the axial center;
The power transmission mechanism according to claim 3, wherein the power transmission shaft is inserted into the hollow portion. The reduction ratio between the fourth rotation element and the third rotation element of the first planetary gear mechanism is the reduction ratio between the eighth rotation element and the seventh rotation element of the second planetary gear mechanism. Set higher than
The power transmission shaft control device controls the power transmission shaft to the first position in a region where the rotational speed of the driven device is relatively low, and a region where the rotational speed of the driven device is relatively high The power transmission mechanism according to any one of claims 1 to 4, wherein the power transmission shaft is controlled to the second position. The first and second planetary gear mechanisms are cycloid reducers,
The fourth and eighth rotating elements are eccentric bodies having an eccentric portion,
The second and sixth rotating elements have a waveform on the outer periphery, and are formed with a through hole into which the eccentric body is inserted and another through hole disposed on the radially outer side of the through hole, A curved plate that rotates around the rotation axis along with the rotation of the drive source,
The first and fifth rotating elements are outer pins that engage with the outer periphery of the curved plate and cause the curved plate to generate the rotational motion,
The power transmission mechanism according to any one of claims 1 to 5 , wherein the third and seventh rotating elements are inner pins that are inserted into the other through holes. A driving source;
A driven device driven by the drive source ;
A speed change mechanism that is driven by the drive source and transmits power with a change in speed change ratio between the drive source and the driven device;
With
The speed change mechanism has first and second planetary gear mechanisms,
The first planetary gear mechanism is
A first rotating element, a second rotating element, a third rotating element, and a fourth rotating element that perform differential rotation with each other;
Have
The third rotating element supports the second rotating element so as to revolve,
The second rotating element is in contact with the first rotating element and the fourth rotating element ;
Before Symbol the second planetary gear mechanism,
A fifth rotating element, a sixth rotating element, a seventh rotating element, and an eighth rotating element that perform differential rotation with respect to each other;
Have
The seventh rotating element supports the sixth rotating element so that it can revolve,
The sixth rotating element is a power transmission mechanism that contacts the fifth rotating element and the eighth rotating element,
The rotation axes of the first and second planetary gear mechanisms are arranged on the same line,
The third and seventh rotating elements are connected to each other;
The driven device is connected to the third and seventh rotating elements;
The first and fifth rotating elements are disposed so as to be restricted from rotating about the rotation axis,
One end side is connected to the drive source, and the other end side includes a power transmission shaft that is switchably connected to the fourth or eighth rotating element,
Between the power transmission shaft and the fourth rotating element, unidirectional rotational power transmission means for transmitting the rotational power in the forward direction of the power transmission shaft and not transmitting the rotational power in the reverse direction is disposed,
The reduction ratio of the first planetary gear mechanism is set higher than the reduction ratio of the second planetary gear mechanism,
In the power transmission shaft control device for controlling the power transmission shaft, the power transmission shaft is disconnected from the eighth rotation element at the first position, and the power transmission shaft is rotated at the eighth position at the second position. A power transmission mechanism that is controlled to be connected to an element.

Images