JP2018132122A - Rotation transmission device using bidirectional clutch by idle gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotation transmission device that has a planetary gear body between an input shaft and an output shaft, and can switch between functions for blocking and allowing a rotation transmission from the output shaft to the input shaft.SOLUTION: An input shaft 2 and an output shaft 3 are provided in a housing 1. A sun gear SG is fixed to the output shaft 3 and an outer surface cum 21 is fixed to the input shaft 2. Also, a planetary gear body 4 having a planetary gear PG which engages with the sun gear SG is axially supported on a carrier 5 and provided around the outer surface cum 21. A projection PJ is formed on the planetary hear body 4, and a control cum 6 for preventing an autorotation thereof is provided outside the planetary gear body 4. When the input shaft 2 is rotated, the autorotation of the planetary gear body 4 is inhibited by the outer surface cum 21 and the rotation is transmitted to the output shaft 3. When the output shaft 3 is rotated, a position of the control cum 6 is changed to control whether or not to allow the autorotation of the planetary gear body 4, so as to switch between the functions for blocking and allowing a rotation transmission to the input shaft 2.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a rotation transmission device that changes a rotation transmission state between an input shaft and an output shaft, and in particular, transmits rotation from the input shaft to the output shaft, and transmission of rotation from the output shaft to the input shaft The present invention relates to a rotation transmission device capable of switching between a free type bidirectional clutch mode in which a shaft is idled and shut off and a mode in which reverse input from an output shaft can also be transmitted.

  In a power transmission system that drives a mechanical device or work equipment from a drive source such as a motor, various transmission devices are used to correspond to the characteristics of the driven device. Among such transmission devices, what is called a “free type bidirectional clutch (or reverse input cutoff clutch)” is used to transmit power from the input shaft (drive side) to the output shaft (driven side). Both forward and reverse rotations are transmitted to the output shaft, and transmission in the opposite direction from the output shaft to the input shaft has a function of causing the output shaft to idle and shut off.

  As an example, the free type bidirectional clutch can be applied to an open / close driving device that can manually operate a hoisting type electric curtain or the like. In this case, the free type bidirectional clutch is interposed between the drive motor and the curtain winding mechanism, and the drive motor is connected to the input shaft and the winding mechanism is connected to the output shaft. When the drive motor is rotated forward / reversely, the curtain can be raised and lowered, and at the stop position of the drive motor, the manual hoisting mechanism can be operated. Disconnected and does not adversely affect the drive motor.

As a free type bidirectional clutch, the present applicant has created a bidirectional clutch of Patent Document 1 below, which will be described with reference to FIGS.
As shown in the longitudinal sectional view at the center of FIG. 6, this free type bidirectional clutch includes an input shaft IS and an output shaft OS arranged at the center of a fixed housing HG having a circular cross section. A cam body CB is fixed to the output shaft OS, and a sun gear SG is fixed to the output shaft OS. The cam body CB and the sun gear SG are disposed adjacent to and opposed to each other in the axial direction. As shown in the cross section AA, the cross section of the cam body CB has a substantially regular triangular shape, and the outer periphery of the cross section is Three straight portions that are sides of a regular triangle are formed.

  Inside the housing HG, three planetary gear bodies PB that form planetary gears PG (cross section BB) that mesh with the sun gear SG of the output shaft OS are arranged at equal intervals in the circumferential direction. The number of planetary gear bodies PG is the same as the number of sides of the cam body CB fixed to the input shaft IS, and each planetary gear body PG is located at the approximate center of the side of the cam body CB. The three planetary gear bodies PB are pivotally supported on the support shaft SS of the carrier CA that can rotate around the central axis o, similarly to the planetary gear of a general planetary gear mechanism. Note that the tip of the support shaft SS is fitted into a disk-shaped carrier auxiliary plate CR, and this carrier auxiliary plate CR is also coupled to the carrier CA by the connecting piece CL and abuts against the end plate portion of the housing HG. However, it can rotate integrally with the carrier CA.

  Each planetary gear body PG is provided with a projecting portion PJ (cross section AA) projecting in the axial direction, and this projecting portion PJ is input when the planetary gear body PB is assembled inside the housing HG. It is provided at an axial position where it comes into contact with the cam body CB of the shaft IS. The cross-sectional shape of the protruding portion PJ is a regular hexagon, and six straight portions that are sides of a regular hexagon are formed on the outer periphery of the cross section. And in the state of the cross section AA in which the protrusion part PJ opposes the center of the side of the cam body CB, a slight gap exists between the protrusion part PJ and the cam body CB, and the rotation of the protrusion part PJ is allowed. Thus, the relative positions of the planetary gear body PB and the cam body CB are set.

FIG. 7A shows the movement of each part when the input shaft is rotated and FIG. 7B shows the movement of each part when the output shaft is rotated with respect to the operation of the free type bidirectional clutch of FIG. ) And will be described.
When the input shaft IS is rotated counterclockwise (as viewed from the right in the central longitudinal sectional view of FIG. 7) by a drive source motor, for example, the regular triangular cam body CB is also rotated counterclockwise. . As a result, as shown in the cross section AA of FIG. 7A, one side (straight portion) of the cam body CB and one side (straight portion) of the regular hexagonal cross section of the projecting portion PJ of the planetary gear body PB are formed. It overlaps linearly. In this state, the overlapping side portions are entirely in surface contact and the planetary gear body PB cannot rotate, and the planetary gear body PB and the carrier CA rotate integrally with the input shaft IS. Further, the output shaft OS meshed with the planetary gear body PB by the sun gear SG also rotates integrally with the movement of the planetary gear body PB (revolution around the central axis o) as shown in the cross section BB.

  That is, the rotation of the input shaft IS rotates the output shaft OS through the planetary gear PG and the sun gear SG of the planetary gear body PB, and the driving force is applied to the driven device connected to this, for example, a lifting device such as a curtain. Communicated. The transmission of this driving force that locks the members interposed between the input and output shafts such as the planetary gear body PB and the carrier CA is the same even when the rotation direction of the input shaft IS is the reverse clockwise direction. And since it is torque transmission by the surface contact of the overlapping linear part, in the free type bidirectional clutch of FIG. 6, large torque transmission is possible.

On the other hand, as shown in the section BB in FIG. 7B, the sun gear SG fixed to the output shaft OS is counterclockwise (viewed from the right in the central longitudinal section in FIG. 7). Is rotated, the rotational torque of the rotation is applied to the planetary gear PG meshing therewith.
Due to this rotational torque, the planetary gear body PB slightly moves relative to the input shaft IS as shown in the cross section AA of FIG. 7B, and the projecting portion PJ is positioned at the center of the side of the cam body CB. Then, the planetary gear body PB can freely rotate. That is, the distance from the center of the planetary gear body PB to the cam body CA is larger than the radius of the circumscribed circle of the projecting portion PJ. Therefore, even if the sun gear SG rotates due to the rotation of the output shaft OS, the carrier CA The shaft-supported planetary gear body PB only rotates (idling), the input shaft IS does not rotate, and transmission of rotational power is interrupted.

Japanese Patent No. 59268433 Japanese Patent Laid-Open No. 2006-43909

  As described above, the free type bidirectional clutch shown in FIG. 6 is capable of transmitting a large torque while having a compact configuration, and protects the motor, etc. of the drive source when there is an unexpected reverse input from the output shaft side. It is also possible to do. However, some of the rotation transmission devices used in various power transmission systems are not limited to the function as a free type bidirectional clutch, for example, while normally blocking the reverse input from the output shaft, In some cases, a rotation transmission device that enables power transmission (reverse input) from the output shaft to the input shaft is required.

  As an example of such a rotation transmission device, a transmission device mounted on a so-called hybrid vehicle that can be driven from both an engine and a motor disclosed in Patent Document 2 described above can be cited. In this hybrid vehicle, as shown in FIG. 8, the front wheel FW is driven by an engine EG and the rear wheel RW is driven by a motor M / G, but the motor M / G that drives the rear wheel RW is an electric generator. When the vehicle is braked or traveling downhill, the motor M / G is driven from the rear wheel RW to operate the generator, and the traveling energy is regenerated in the form of electric power. Therefore, a one-way clutch OW and a connecting / disconnecting mechanism CT are installed between the motor M / G (input side) and the rear wheel RW (output side). The M / G is disconnected to prevent the motor M / G from being rotated, and the regenerative brake is applied by connecting the rear wheel RW and the motor M / G when the vehicle is braked.

That is, the one-way clutch OW and the connecting / disconnecting mechanism CT described in Patent Document 2 is a rotation transmission device in which a function that allows reverse input from the output shaft to the input shaft when necessary is added to the free type bidirectional clutch. It is. However, the thing of patent document 2 has the problem that the structure of apparatus itself and the structure for switching control of power transmission are complicated, and an apparatus enlarges.
An object of the present invention is to construct a multifunctional rotation transmission device that utilizes the compact free-type two-way clutch of FIG. 6 and can be used, for example, in the power transmission system of a hybrid vehicle shown in FIG. is there.

In view of the above problems, the rotation transmission device of the present invention has a free type bidirectional clutch of FIG. 6 as a basic structure, and a control gear body and a control cam body are added thereto, and the control gear body, the control cam body, By providing a switching member that connects and disconnects rotation transmission between the output shaft, it is possible to switch between a mode in which the output shaft idles and the rotation transmission to the input shaft is cut off, and a mode in which rotation is transmitted from the output shaft to the input shaft It is what. That is, the present invention
“A non-rotatable housing (1), an input shaft (2) and an output shaft (3) rotatable around a common central axis in the housing (1). The rotation in the reverse direction is transmitted to the output shaft (3), and the transmission of the rotation from the output shaft (3) to the input shaft (2) is interrupted by the idle rotation of the output shaft (3). A rotation transmission device capable of switching between a mode and a mode in which rotation is transmitted,
The outer cam body (21) fixed to the input shaft (2), the sun gear (SG) fixed to the output shaft (3), and the planetary gear (PG) meshing with the sun gear (SG). A planetary gear body (4) and a carrier (5) that rotatably supports the planetary gear body (4) and rotates around a common central axis;
The planetary gear body (4) is provided with a protrusion (PJ) that protrudes in the axial direction and contacts the outer surface cam body (21).
When the input shaft (2) rotates, the outer surface cam body (21) and the projecting portion (PJ) come into contact with each other, and rotation of the planetary gear body (4) is prevented and the output shaft (3) is prevented from rotating. When the rotation is transmitted while the output shaft (3) rotates, the contact between the projecting portion (PJ) and the outer surface cam body (21) is released, and the planetary gear by the sun gear (SG) is released. The planetary gear body (4) and the outer surface cam body (21) are arranged so that rotation of the body (4) is allowed and transmission of rotation to the input shaft (2) is interrupted,
A control gear body (7) having an internal gear (RG) meshing with the planetary gear (PG) of the planetary gear body (4) and rotatable about a common central axis; and the planetary gear body (4) A control cam body (6) having an inner peripheral cam surface (61) capable of abutting against the projecting portion (PJ) and rotatable about a common central axis, and the control gear body ( 7) and a switching member (8) for connecting and disconnecting the rotation transmission between the control cam body (6), and
When the switching member (8) is in a rotation transmission state, when the output shaft (3) rotates, the inner peripheral cam surface (61) of the control cam body (6) and the protrusion (PJ) come into contact with each other. The rotation of the planetary gear body (4) is prevented, and the rotation is transmitted to the input shaft (2). "
The rotation transmission device is characterized by the above (in order to facilitate understanding, reference numerals in the attached drawings are shown in parentheses).

  A linear portion is formed in each of the cross section of the projecting portion (PJ) and the cross section of the outer surface cam body (21), and when the rotation is transmitted from the input shaft (2) to the output shaft (3), the linear portion It is preferable that the two are in contact with each other. Further, when the curved portion is formed in the cross section of the outer cam body (21) and rotation is transmitted from the output shaft (3) to the input shaft (2), the protruding portion (PJ) is formed on the curved portion. It is preferable to configure so that they abut.

  A spring (9) is installed between the carrier (5) and the control cam body (6), and the control cam body (6) rotates the planetary gear body (4) by the sun gear (SG). It is preferable to be configured so as to be pressed to a position that allows the

  Further, external teeth are formed on the outer circumferences of the control gear body (7) and the control cam body (6), respectively, and the control gear (82) that can mesh with the external teeth as the switching member (8). ) And the control gear (82) can be rotatably supported on the housing (1).

  The cross sections of the protrusion (PJ) and the outer surface cam body (21) are regular polygonal shapes (regular polygons or shapes similar thereto), and the planetary gear body (4) includes the outer surface cam body (21). It is preferable to arrange the same number of sides as the number of sides of the cross section in the circumferential direction at equal intervals.

In the rotation transmission device of the present invention, an input shaft and an output shaft that are rotatable around a common central axis are installed in a fixed housing, and a sun gear concentric with the output shaft is fixed to the output shaft. A pair of planetary gear bodies having meshing planetary gears are arranged, and the planetary gear bodies are rotatably supported on a carrier. The planetary gear body is provided with a protruding portion that protrudes in the axial direction, and the input shaft is provided with an outer surface cam body that comes into contact with the protruding portion.
That is, the rotation transmission device of the present invention has a structure of a free type bidirectional clutch shown in FIG. 6 as a basic structure, and a mode switching mechanism including a control gear body, a control cam body, and the like is added thereto. is there. Therefore, the rotation transmission device of the present invention has a mode in which it operates as a free type bidirectional clutch. In this mode, as in the case of the free type bidirectional clutch shown in FIG. The rotation of the planetary gear body is constrained by contact between the outer surface cam body and the outer surface cam body, and the input shaft, the planetary gear body, the carrier and the sun gear are integrated in a so-called glued state, and the rotation is transmitted to the output shaft. . On the other hand, when the output shaft is rotated, the planetary gear body is slightly moved by the rotation of the sun gear, and the planetary gear body is allowed to rotate, and the rotation is not transmitted to the input shaft. The output shaft will idle. Therefore, when the rotation transmission device of the present invention is applied to, for example, the hybrid vehicle shown in FIG. 8, the rotation transmission from the rear wheel to the motor M / G is interrupted to prevent the motor M / G from rotating, Power loss of the driving engine can be avoided.

  Incidentally, when operating as a free type bidirectional clutch, the control gear body in the mode switching mechanism has its internal gear meshed with the sun gear via the planetary gear of the planetary gear body. (However, the rotation direction is opposite to the output shaft). At this time, the control cam body is held at a position where the inner peripheral cam surface formed on the control cam body does not come into contact with the projecting portion of the planetary gear body and remains stopped.

  As will be described in detail later with reference to FIG. 5 and the like, when the mode switching mechanism including the switching member is switched so that the rotation transmission state is established between the control gear body and the control cam body, the idle control (rotation) is performed. The control cam body rotates around a common rotation axis by the gear body. When the control cam body rotates slightly, its inner peripheral cam surface comes into contact with the projecting portion of the planetary gear body from the outside to prevent the planetary gear body from rotating. The planetary gear body, which is prevented from rotating, rotates (revolves) together with a carrier or the like around a common rotating shaft. Immediately after that, the inner part of the projecting portion of the planetary gear body is an outer surface cam of the input shaft. Rotate while pressing against the body. Thus, in the mode after switching (reverse input mode), the rotating member (including the control gear body and the control cam body) between the output shaft and the input shaft is integrated and input from the output shaft. The rotation is transmitted to the shaft.

  As described above, in the rotation transmission device of the present invention, by operating the switching member, the function of the free type bidirectional clutch that idles the output shaft to block the reverse input and the reverse transmission that transmits the rotation from the output shaft to the input shaft. For example, when the present invention is applied to a hybrid vehicle, the regenerative brake can be operated to recover travel energy. At that time, the rotation transmission from the input shaft to the output shaft and the rotation transmission that is the reverse input are performed in a state where the rotating members such as the planetary gear body and the carrier are integrated, so the transmission torque is limited by the frictional force or the like. However, the rotation transmission device of the present invention is suitable for a power transmission device that drives a device having a large load torque. Further, since transmission / interruption of rotation is switched depending on whether the rotation of the planetary gear body is prevented or allowed, the structure is compact, and in particular, the axial length can be shortened.

  In the invention of claim 2, linear portions are respectively formed in the cross section of the projecting portion of the planetary gear body and the cross section of the outer surface cam body of the input shaft, and the rotation of the planetary gear body is constrained to transmit the rotation from the input shaft to the output shaft. When doing so, the rotation of the planetary gear body is prevented by bringing the linear portions into contact with each other. If it carries out like this, plane parts will press-contact with the part which contact | abuts, a big force can be transmitted, and the transmission torque from an input shaft to an output shaft can be increased.

According to the invention of claim 3, when a curved portion is formed in the cross section of the outer cam body of the input shaft and rotation is transmitted from the output shaft to the input shaft (reverse input mode), the curved portion is projected from the planetary gear body. It contacts the part. The curved portion is provided for the following reason.
In the reverse input mode, with the rotation of the planetary gear body restricted, the projection of the planetary gear body abuts the outer cam body and the input shaft is rotated while pushing the outer cam body. When switching to the direction clutch operation, it is necessary to immediately release the restraint of the planetary gear body and allow the rotation. After forming the curved portion on the outer cam body, for example, the curved portion that becomes the envelope of the cross section of the projecting portion when the planetary gear body rotates, and contacting this with the projecting portion, after the reverse input mode ends, Thus, the planetary gear body can be reliably rotated (idled).

  According to a fourth aspect of the present invention, a spring is installed between the carrier and the control cam body, and the control cam body is pressed to a position that allows the planetary gear body to rotate by the sun gear. The control cam body is a member provided to prevent rotation by engaging the inner peripheral cam surface with the projecting portion of the planetary gear body in the reverse input mode, and in the free type bidirectional clutch mode, the projecting portion. Must be prevented from engaging. If the spring is installed between the control cam body and the carrier as in the invention of claim 4, even if vibration or the like occurs during the operation of the rotation transmission device, the inner peripheral cam surface of the control cam body is the planetary gear body. It can hold | maintain reliably in the position which does not engage with the protrusion part.

  The invention of claim 5 relates to a mode switching mechanism, wherein external teeth are formed on the outer circumferences of the control gear body and the control cam body, and a control gear capable of meshing with each external tooth is provided on the switching member. It is installed and configured to rotatably support the control gear on the housing. According to this, at the time of switching to the reverse input mode, rotation is transmitted from the control gear body to the control cam body by gear coupling, so that the inner peripheral cam surface of the control cam body is strongly against the projecting portion of the planetary gear body. The planetary gear body is prevented from rotating unexpectedly by being pressed. Further, since the control gear of the switching member is rotatably supported by the fixed housing, the centrifugal force does not act during transmission of rotation from the output shaft in the reverse input mode to the input shaft. Therefore, it is possible to prevent disturbances in the control state caused by centrifugal force, such as unexpected mode switching during operation in the reverse input mode.

  The invention according to claim 6 is a planetary gear body in which the shape of the cross section of the projecting portion and the outer surface cam body is a regular polygon shape, that is, a regular polygon shape or a shape approximate thereto, and is arranged around the outer surface cam body. The same number of sides as the number of sides of the cross section of the outer cam body are arranged at equal intervals in the circumferential direction. With such a configuration, the rotating member is arranged in a uniform state around the input / output shaft, and generation of vibration due to unbalanced force can be prevented.

1 is a structural diagram showing the overall structure of an embodiment of a rotation transmission device of the present invention. It is an exploded view which shows the main components of the rotation transmission apparatus of FIG. It is a figure which shows the external appearance of the rotation transmission apparatus of FIG. It is a figure explaining the action | operation of the mode which interrupts | blocks the reverse input of the rotation transmission apparatus of FIG. It is a figure explaining the operation | movement of the mode in which reverse input of the rotation transmission apparatus of FIG. 1 is possible. It is a figure which shows an example of the conventional free type bidirectional clutch. It is a figure which shows the action | operation of the free type bidirectional clutch of FIG. It is a figure which shows an example of the power transmission system of a hybrid vehicle.

  Hereinafter, a rotation transmission device of the present invention will be described with reference to the drawings. FIG. 1 shows the overall structure of an embodiment of the rotation transmission device of the present invention, and FIG. 2 shows the main components in a single state as an exploded view. FIG. 3 shows an external structure of the rotation transmission device of the embodiment in a mode in which reverse input is possible.

As shown in FIG. 1 (see also FIG. 3), the rotation transmission device of this embodiment can rotate around a common central axis o arranged at the center of a fixed housing 1 whose outer shape is substantially square. An input shaft 2 and an output shaft 3 are provided. Rolling bearings BG are mounted between the input shaft 2 and output shaft 3 and the housing 1.
The housing 1 is divided into a housing body 11 having a space 1S having a circular cross section and a shield body 12 fixed to the housing body 11 so as to close the space 1S. The space 1S includes a planetary gear body. 4. Rotating members such as the carrier 5 are accommodated. As shown also in FIG. 3, the housing 1 is provided with a notch opening 1O cut out over an angle range of 90 °, and the notch opening 1O has a control gear body 6 and a control cam. The gears 6G and 7G formed on the outer periphery of the body 7 are exposed, and a switching member 8 for connecting and disconnecting rotation transmission between both gears is installed. These members constitute a mode switching mechanism described later in the rotation transmission device of the present invention.

An outer surface cam body 21 is integrally fixed to the input shaft 2. As shown in the cross section AA of FIG. 1 (see also FIG. 2), the cross section of the outer cam body 21 has a shape approximating a regular triangle with the tip portion cut off. Three sides having 21A and a curved portion 21B are formed.
A sun gear SG is fixed to the output shaft 3 as shown in a cross section BB (see also FIG. 2). The outer surface cam body 21 of the input shaft 2 and the sun gear SG of the output shaft 3 are disposed adjacent to and opposite to each other in the axial direction so that the side portions of the two are in surface contact (cross section CC).

  Around the input shaft 2 and the output shaft 3, three planetary gear bodies 4 forming planetary gears PG (cross section BB in FIG. 1) meshing with the sun gear SG are arranged at equal intervals in the circumferential direction. Established. The number of planetary gear bodies 4 is the same as the number of sides of the outer surface cam body 21 of the input shaft 2, and each planetary gear body 4 is located at the approximate center of the side of the outer surface cam body 21. As shown in FIG. 2, the three planetary gear bodies 4 are rotatably supported on a support shaft 51 erected on a disk-shaped carrier 5 via a slide bearing (not shown). The central circular hole 52 is fitted in the input shaft 2 and is rotatable around the central axis o.

  Each planetary gear body 4 is provided with a projecting portion PJ (cross section AA in FIG. 1) projecting in the axial direction, and this projecting portion PJ places the planetary gear body 4 inside the space portion 1S of the housing 1. When it is assembled, it is provided at an axial position where it abuts on the outer surface cam body 21 of the input shaft 2. The cross-sectional shape of the protruding portion PJ is a regular hexagon, and six straight portions that are sides of a regular hexagon are formed on the outer periphery of the cross section. And in the state of the cross section AA in which the protrusion part PJ opposes the center of the side of the outer surface cam body 21, a slight gap exists between the protrusion part PJ and the outer surface cam body 21, and the rotation of the protrusion part PJ occurs. The relative position between the planetary gear body 4 and the outer surface cam body 21 is set so that is allowed.

  As described above, the rotation transmission device of the present invention has a structure equivalent to the free type bidirectional clutch shown in FIG. 6 as a basic structure, and as described later, a free type that blocks reverse input from the output shaft 3 side. The bidirectional clutch can be operated. Furthermore, the rotation transmission device of the present invention is provided with a mode switching mechanism that enables transmission of rotation from the output shaft 3 to the input shaft 2. Here, the structure of the mode switching mechanism will be described.

The mode switching mechanism is configured to rotate between the control cam body 6 displayed on the section AA in FIG. 1, the control gear body 7 displayed on the section BB, and the control cam body 6 and the control gear body 7. And a switching member 8 for connecting and disconnecting transmission.
The control cam body 6 is disposed at the same axial position as the outer surface cam body 21 of the input shaft 2, and has a space portion in which an inner peripheral cam surface 61 surrounding the projecting portion PJ of the planetary gear body 4 is formed. Yes. Further, as shown in FIG. 2, three fan-shaped guide grooves 62 are formed in the circumferential direction, and the guide grooves 62 are fitted to fan-shaped guide protrusions 53 erected on the disk-shaped carrier 5. The The circumferential length of the guide groove 62 is longer than that of the guide protrusion 53, and a coil spring 9 is inserted in the gap between the two so that the control cam body 6 rotates clockwise with respect to the carrier 5. It is pressed by the coil spring 9. A straight part 61A and a circular arc part 61B are formed on the inner circumferential cam surface 61 surrounding the projecting part PJ of the planetary gear body 4, and the projecting part PJ of the planetary gear body 4 in the state of the section AA in FIG. However, the rotation (spinning) can be performed without contacting the inner circumferential cam surface 61 and the outer cam body 21.

  The control gear body 7 is disposed at the same axial position as the sun gear SG of the output shaft 3, and has a ring-shaped internal tooth RG that meshes with the planetary gear PG of the planetary gear body 4. External teeth 6G and 7G are formed on the outer circumferences of the control cam body 6 and the control gear body 7, respectively. Therefore, the control gear body 7 has an internal tooth RG formed inward and outward. It is an annular member in which external teeth 7G are formed.

  As shown in FIG. 3, the external teeth 6G of the control cam body 6 and the external teeth 7G of the control gear body 7 are partially exposed to the outside of the housing 1 through the notch opening 1O. A switching member 8 is attached to the portion 1O. The switching member 8 includes a lever 81 pivotally attached to the housing 1 and a control gear 82 attached to the tip of the lever 81. When the lever 81 is in the position shown in FIG. 1, the control cam body 6 and the control gear body 7 are separated, but when the control gear 82 is engaged with the external teeth 6G and the external teeth 7G as shown in FIG. The rotation of the control gear body 7 is transmitted to the control cam body 6 via the control gear 82.

Next, the operation of the rotation transmission device of the present invention will be described with reference to FIGS. In these drawings, the housing is omitted for easy understanding.
FIG. 4 is a diagram for explaining the operation when the rotation transmission device of the present invention is set to the free type bidirectional clutch mode and the reverse input from the output shaft 3 is cut off. FIG. FIG. 4B is a diagram illustrating the movement of each component when the output shaft 3 is rotated. In the free type bidirectional clutch mode, the control gear 82 of the switching member 8 is placed at the position shown in FIG. 4, and the control cam body 6 and the control gear body 7 are disconnected.

As shown in the longitudinal sectional view of FIG. 4A, when the input shaft 2 is rotated in the clockwise direction (viewed from the right), the regular triangular outer cam body 21 is also rotated in the clockwise direction. As shown in the section AA of a), the straight portion 21A on the side of the outer cam body 21 and the one side of the regular hexagonal section in the projecting portion PJ of the planetary gear body 4 are linearly overlapped. In this state, the overlapping side portions are entirely in surface contact with each other to prevent the planetary gear body 4 from rotating, and the planetary gear body 4 and the carrier 5 rotate together with the input shaft 2. The output shaft 3 meshing with the planetary gear body 4 also rotates integrally around the central axis o as shown in the cross section BB.
When the input shaft 2 rotates counterclockwise (viewed from the right), the curved portion 21B on the side of the outer cam body 21 comes into contact with the two apexes in the regular hexagonal cross section of the protruding portion PJ. At this time, since the planetary gear body 4 cannot rotate, the planetary gear body 4 and the carrier 5 rotate together with the input shaft 2, and the output shaft 3 also forms a counterclockwise around the central axis o. Rotate in the direction. When the input shaft 2 rotates, the control cam body 6 and the control gear body 7 also rotate together with the planetary gear body 4 and the carrier 5 in a so-called glued state.

On the other hand, as shown in the longitudinal sectional view of FIG. 4B, when the output shaft 3 rotates in the clockwise direction (viewed from the right), the rotational torque of the rotation is applied to the planetary gear PG meshing with the sun gear SG. Is granted. Due to this rotational torque, the planetary gear body 4 rotates slightly, and the relative position between the planetary gear body 4 and the outer surface cam body 21 changes, and as shown in the cross section BB of FIG. PJ is located at the center of the side of the outer cam body 21. In this state, the distance from the center of the protrusion PJ to the outer cam body 21 is larger than the radius of the circumscribed circle of the protrusion PJ, and the planetary gear body 4 can freely rotate. That is, even if the sun gear SG is rotated by the output shaft 3, the planetary gear body 4 that is pivotally supported by the carrier 5 only rotates, and transmission of rotational power to the input shaft 2 is interrupted. This is the same even if the rotation direction of the output shaft 3 is counterclockwise.
When the output shaft 3 is rotated, the control gear body 7 meshing with the sun gear SG is rotated in the reverse direction via the planetary gear PG, but the control cam body 6 is a position where the planetary gear body 4 is allowed to rotate. This position is held by pressing the control cam body 6 clockwise against the carrier 5 by the coil spring 9 and abutting the end face of the guide groove 62 against the end face of the guide projection 53. The

  Thus, in the free type bidirectional clutch mode of the rotation transmission device of the present invention, the rotation from the input shaft 2 is transmitted to the output shaft 3 as well as the output shaft 3 as in the free type bidirectional clutch of FIG. Reverse input from is interrupted by idling the output shaft. When the rotation transmission device of the present invention is applied to the hybrid vehicle of FIG. 8 and the input shaft 2 is connected to the motor M / G and the output shaft 3 is connected to the rear wheel RW, the motor M / G is connected to the motor M / G by a battery or the like. Electric energy can be supplied to drive the rear wheel RW to drive the vehicle or assist driving by the engine EG. Further, in a situation where the power of the engine EG is sufficient and reverse input from the rear wheel RW occurs, the rear wheel RW can be idled to prevent engine EG power loss due to the accompanying rotation of the motor M / G.

  Next, the rotation transmission from the output shaft 3 to the input shaft 2, that is, the operation at the time of switching to the reverse input mode capable of reverse input will be described with reference to FIG. FIG. 5A is a diagram showing the movement of each component that occurs at the beginning when switching to the reverse input mode. FIG. 5B shows the rotation transmitted from the output shaft 3 to the input shaft 2 in the reverse input mode. It is a figure showing a mode to do.

To switch to the reverse input mode, first, the lever 81 of the switching member 8 is rotated to place the external gear 82 at the position shown in FIG. As a result, the external teeth 6G and 7G formed on the outer periphery of the control cam body 6 and the control gear body 7 are gear-coupled, and the rotation of the control gear body 7 is transmitted to the control cam body 6.
As described above, in the free type bidirectional clutch mode in which the output shaft 3 is idled, the control gear body 7 rotates in the direction opposite to that of the output shaft 3, as shown in the cross section BB in FIG. In addition, when the output shaft 3 rotates in the clockwise direction (viewed from the right), the control gear body 7 rotates in the counterclockwise direction. When the rotation of the control gear body 7 is transmitted to the control cam body 6 by the control gear 82, the control cam body 6 also rotates slightly counterclockwise while compressing the coil spring 9 (see the broken line arrow in FIG. 5A). 5A, the straight portion 61A of the inner peripheral cam surface 61 formed on the control cam body 6 has a regular hexagonal cross section of the projecting portion PJ of the planetary gear body 4. As shown in FIG. Abuts with one side. In this state, the rotation of the planetary gear body 4 is restricted.

  After the rotation of the planetary gear body 4 is constrained, the sun gear SG, the planetary gear body 4 and the carrier 5 of the output shaft 3 are glued, and these are the control cam body 6 and the control gear body which are also glued. 7 and rotate clockwise. Immediately after that, as shown in a cross section AA of FIG. 5B, two apexes in the regular hexagonal section of the projecting portion PJ of the planetary gear body 4 are formed on the outer cam body 21 of the input shaft 2. It contacts the curved portion 21B of the side. As a result, the input shaft 2 is also rotated in the clockwise direction in such a manner that the outer cam body 21 is pushed clockwise by the projecting portion PJ of the planetary gear body 4. That is, in the reverse input mode, the rotating members from the output shaft 3 to the input shaft 2 including the control cam body 6 and the control gear body 7 rotate as a unit, and the rotation is transmitted from the output shaft 3 to the input shaft 2. The

  In the above application example in which the rotation transmission device of the present invention is applied to the hybrid vehicle of FIG. 8, the rotation transmission device is switched to the reverse input mode by operating the switching member 8 when the vehicle is braking or traveling downhill. As a result, the rear wheel RW that was disengaged in the free type bidirectional clutch mode is connected to the motor M / G, and the motor M / G is operated as a generator to collect travel energy during braking, etc., in the battery. In addition, a regenerative brake can be applied to the vehicle.

In the embodiment of the present invention shown in FIG. 5 (and FIG. 1 etc.), a curved portion 21B is provided around the outer surface cam body 21 of the input shaft 2, and in the reverse input mode, the regular hexagonal cross section 2 The apexes are brought into contact with the curved portion 21 </ b> B, and rotation is transmitted from the output shaft 3 to the input shaft 2. The curved portion 21B is formed in order to quickly and surely return when the switching member 8 is returned to return from the reverse input mode to the free type bidirectional clutch mode. That is, the curved portion 21B of the outer surface cam body 21 is a curve that approximates the envelope of the cross section of the projecting portion PJ when the planetary gear body 4 rotates, and when the planetary gear body 4 rotates, In addition, the rotation of the output shaft 3 is not restricted by the outer cam body 21, and the output shaft 3 can be easily idled.
The reason why one curved portion 21B of the outer cam body 21 is formed on each side is that the rotation direction in the reverse input mode is often determined to be one direction. For example, when applied to a hybrid vehicle, it is sufficient to recover energy only when the vehicle is traveling forward, and there is no need to consider rotation in the opposite direction. However, it is obvious that the rotation device of the present invention can transmit rotation to the input shaft 2 regardless of the rotation direction of the output shaft 3.

  Further, in the embodiment of FIG. 5 and the like, the control gear body 6 and the control gear 82 that meshes with the external teeth 6G and 7G of the control cam body 7 are installed, and the lever 81 to which the control gear 82 is attached is operated to rotate. Switches between bidirectional clutch mode and reverse input mode. Since the lever 81 is supported by the fixed housing 1, centrifugal force does not act when the input shaft 2 and the output shaft 3 are rotated. For this reason, it is possible to prevent the control state from being disturbed due to centrifugal force, such as unexpected mode switching.

As described above in detail, in the rotation transmission device of the present invention, the planetary gear body is installed between the input shaft and the output shaft, and when the output shaft is rotated, the planetary gear body is idled to the input shaft. A free type bidirectional clutch that cuts off rotation transmission has a basic structure, and by providing a switching mechanism with a control gear body and control cam body on this, a mode in which rotation transmission to the input shaft is cut off and from the output shaft The mode can be switched to a mode in which rotation is transmitted to the input shaft. Therefore, the rotation transmission device of the present invention is applicable not only to a hybrid vehicle but also to a general power transmission device. For example, in a so-called electric assist bicycle equipped with a motor that assists human power, when traveling downhill, etc. In addition, the present invention can be applied to a power transmission device in which the motor is driven as a generator for energy regeneration.
In the above embodiment, the control gear body and the control cam body are formed with external teeth, respectively, and the switching mechanism is provided with a control gear meshing with these, and the rotation transmission is performed by gear coupling. Since rotational torque transmitted from the shaft to the input shaft does not act, a friction wheel may be installed in place of the control gear, and rotation may be transmitted from the control gear body to the control cam body by friction transmission. In addition, the cross-sectional shape of the outer cam body attached to the input shaft is a regular triangle shape, and the control gear body is formed with a regular hexagonal protrusion. Obviously, various modifications can be made to the above-described embodiment, such as adoption.

1: Housing 2: Input shaft 21: External cam body 3: Output shaft 4: Planetary gear body 5: Carrier 6; Control cam body 7: Control gear body 8: Switching member 82: Control gear SG: Sun gear PG: Planet Gear PJ: Projection

Claims (6)

A non-rotatable housing, an input shaft and an output shaft rotatable around a common central axis in the housing; rotation from the input shaft is transmitted to the output shaft; and from the output shaft to the input shaft The rotation transmission to the rotation transmission device can be switched between a mode in which the output shaft is idled and cut off and a mode in which the rotation is transmitted,
An outer cam body fixed to the input shaft, a sun gear fixed to the output shaft, a planetary gear body having a planetary gear meshing with the sun gear, and a planetary gear body rotatably supporting the planetary gear body. With a carrier that can rotate around the central axis,
The planetary gear body is provided with a protrusion that protrudes in the axial direction and contacts the outer surface cam body,
When the input shaft rotates, the outer cam body and the projecting portion come into contact with each other, the rotation of the planetary gear body is prevented and rotation is transmitted to the output shaft, while the output shaft rotates. The planetary gear body and the outer peripheral cam body are released from contact with each other, the rotation of the planetary gear body by the sun gear is allowed, and transmission of rotation to the input shaft is blocked. An outer surface cam body, and
A control gear body that has an internal gear that meshes with the planetary gear of the planetary gear body, and that can rotate around a common central axis; and an inner peripheral cam surface that can come into contact with the protruding portion of the planetary gear body. A control cam body rotatable around a common central axis, and a switching member for connecting and disconnecting rotation transmission between the control gear body and the control cam body are installed,
When the switching member is in a rotation transmission state, when the output shaft rotates, the inner peripheral cam surface of the control cam body and the protrusion come into contact with each other to prevent the planetary gear body from rotating, and to the input shaft. A rotation transmission device characterized in that rotation is transmitted. The straight section is formed in each of the section of the projection and the section of the outer surface cam body, and when rotation is transmitted from the input shaft to the output shaft, the straight sections contact each other. Rotation transmission device. The curved portion is formed in a cross section of the outer surface cam body, and when the rotation is transmitted from the output shaft to the input shaft, the projecting portion comes into contact with the curved portion. The rotation transmission device described. The spring is installed between the said carrier and the said control cam body, The said control cam body is pressed to the position which accept | permits the rotation of the said planetary gear body by the said sun gear. A rotation transmission device according to claim 1. External teeth are formed on the outer circumferences of the control gear body and the control cam body, respectively, and the switching gear is provided with a control gear that can mesh with each external tooth, and the control gear is The rotation transmission device according to any one of claims 1 to 4, wherein the rotation transmission device is rotatably supported by the housing. Cross sections of the projecting portion and the outer surface cam body are each a regular polygonal shape, and the planetary gear body has the same number of sides as the number of sides of the outer surface cam body at equal intervals in the circumferential direction. The rotation transmission device according to any one of claims 1 to 5.