JP2017180580A - Driving force transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a driving force transmission device capable of transmitting driving force even in a case where a rotor relatively rotates in any direction, enabling smooth engagement, and preventing occurrence of looseness.SOLUTION: A cam mechanism 28 of a clutch mechanism 2 is configured to move a first head ball 23 radially outward to rotate a first strut 22; after engaging one end part 22b of the first strut 22 and a first engagement part 20a1 of an input gear 20, move a second heat ball 26 radially outward to rotate a second strut 25; and then engage one end part 25b of the second strut 25 and a second engagement part 20a2 of the input gear 20.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a driving force transmission device capable of switching between a transmission state in which rotation of an input member is transmitted to an output member and a non-transmission state in which rotation is not transmitted.

  Conventionally, a clutch mechanism comprising a strut and a ball that presses the strut against a cylindrical output shaft inserted into the input shaft from a cylindrical input shaft that is rotated by a driving force transmitted from a drive source. There is known a driving force transmission device that transmits rotation via a pin (see, for example, Patent Document 1).

  The clutch mechanism described in Patent Document 1 includes a rotatable strut disposed in an opening formed on the peripheral surface of the output shaft, and a headball that can press the strut from the inside in the radial direction. . In this clutch, when the strut is pressed by the headball, a part of the strut protrudes from the outer peripheral surface of the output shaft and engages with an engaging portion formed on the inner peripheral surface of the input shaft. Thereby, the rotation of the input shaft is transmitted to the output shaft.

  The clutch mechanism configured in this way is a clutch that transmits rotation from the input shaft to the output shaft only when the input shaft rotates to one side with respect to the output shaft when the strut is pressed by the headball (so-called clutch) , One-way clutch).

  Therefore, in the driving force transmission device provided with this clutch mechanism, when the input shaft rotates relative to one side relative to the output shaft, the input shaft rotates integrally with the output shaft and rotates relative to the other side. In this case, the input shaft is idle with respect to the output shaft.

JP2009-074637

  By the way, in the conventional clutch mechanism as described in Patent Document 1, in order to enable the input shaft and the output shaft to rotate integrally even when the input shaft rotates relative to the other side with respect to the output shaft. The clutch mechanism may be provided with a new strut that can be engaged with the input shaft in a direction different from that of the existing strut and a headball for pressing the new strut.

  In this way, when the transmission state in which rotation is transmitted in any direction and the non-transmission state in which rotation is not transmitted in any direction are configured to be switchable, It is necessary to engage the struts so that the engaging portion of the input shaft is fitted between the struts. And in order to engage smoothly, it is necessary to comprise so that sufficient clearance may be formed between the engaging part of a strut and the engaging part of an input shaft in the case of engagement.

  However, if the interval between the strut and the engaging portion is increased in order to ensure sufficient clearance, a large interval exists between the strut and the engaging portion even in the transmission state after the engagement is completed. There was a risk that rattling would occur, causing noise and vibration.

  The present invention has been made in view of the above points, and can transmit a driving force even when one rotating body rotates in any direction with respect to the other rotating body, and can be smoothly engaged. Another object of the present invention is to provide a driving force transmission device in which rattling is unlikely to occur.

  In order to achieve the above object, a driving force transmission device (2) of the present invention is inserted into a cylindrical first rotating body (20) and the first rotating body (20), and the first rotating body ( 20), a cylindrical second rotating body (21) having a first opening (21a) and a second opening (21b) on the peripheral surface, and the first opening (21a). And a first strut (22) fixed to the second rotating body (21) so as to be rotatable about an axis extending in the axial direction of the second rotating body (21), and the first strut (22) is arranged radially inside and is movable in the radial direction, and when moving radially outward, presses one end (22b) of the first strut (22) to support the first strut ( A first pressing member (23) that rotates 22) and moves the one end (22b) radially outward; A second strut (25) disposed in the second opening (21b) and rotatably fixed to the second rotating body (21) about an axis extending in the axial direction of the second rotating body (21). ) And the radially inner side of the second strut (25), is movable in the radial direction, and presses one end (25b) of the second strut (25) when moved radially outward. Then, the second pressing member (26) for rotating the second strut (25) and moving the one end (25b) radially outward, the first pressing member (23) and the second pressing member A cam mechanism (28) for moving the member (26) in the radial direction, and the first rotating body (20) is formed on an inner peripheral surface of the first rotating body (20), and the first strut ( When the one end (22b) of 22) moves radially outward, the one end (22b) A first engaging portion (20a1) that integrally engages the first rotating body (20) and the second rotating body (21) to one side, and the first rotating body (20). When the one end (25b) of the second strut (25) moves radially outward, the first rotating body (20) is engaged with the one end (25b). And a second engaging portion (20a2) for integrally rotating the second rotating body (21) to the other side, and the cam mechanism (28) is one end portion of the first strut (22). (22a2) and the first engagement portion (20a1) are engaged, and one end (25b) of the second strut (25) and the second engagement portion (20a2) are engaged. In making the transmission state, after moving the first pressing member (23) radially outward, the second pressing member (26) is changed to a diameter. It is characterized by being moved outward in the direction.

  As described above, in the driving force transmission device of the present invention, the first engaging portion formed on the first rotating body and the one end portion of the first strut disposed on the second rotating body are engaged with each other. The first rotator and the second rotator are integrally rotatable on one side. On the other hand, the first rotating body and the second rotating body are brought into engagement by engaging the second engaging portion formed on the first rotating body with one end of the second strut disposed on the second rotating body. , And can be rotated integrally to the other side.

  Further, the first pressing member that rotates the first strut and the second pressing member that rotates the second strut are moved in the radial direction by the cam mechanism. The first strut and the second strut are pressed and rotated by the thus moved pressing member, and are engaged with the first engaging portion and the second engaging portion. Thereby, the driving force transmission device is in a transmission state.

  When the cam mechanism is switched from the non-transmission state to the transmission state, after the first pressing member is moved radially outward (that is, after the first strut is engaged with the first engagement portion). The second pressing member is moved radially outward (that is, the second strut having a different orientation from the first strut is engaged with the second engaging portion).

  Thereby, after the position of the engaging portion is determined by the first strut, the second strut is engaged. Therefore, the clearance between the strut and the engagement portion required for engagement can be reduced as compared with the configuration in which two types of struts are engaged simultaneously. As a result, smooth engagement is possible without increasing the clearance.

  Therefore, according to the driving force transmission device of the present invention, the driving force can be transmitted even if one rotating body rotates in any direction with respect to the other rotating body, and smoothly engages and switches to the transmitting state. In addition, it is possible to suppress the occurrence of rattling that causes noise and vibration in the transmission state.

  In the driving force transmission device of the present invention, the cam mechanism (28) is disposed coaxially with the second rotating body (21) inside the second rotating body (21), and the second rotating body. (21) An axially movable cam rod (28a), an actuator (ACT) for moving the cam rod (28a), and the cam rod (28a) are inserted into the cam rod (28a) in the axial direction. And a cam ring (28b) fixed to the cam rod (28a) so that a relative position of the cam ring (28b) with respect to the cam rod (28a) is a predetermined position. And an urging member (28d) that urges the cam ring (28b) in the axial direction, and the cam ring (28b) is in the transmission state on the outer peripheral surface of the cam ring (28b). The cam surfaces (28b1, 28b2) are formed to move the first pressing member (23) and the second pressing member (26) radially outward when moved to the corresponding position. Also good.

Sectional drawing which shows the structure of the clutch mechanism of the vehicle which concerns on embodiment. 2A and 2B are cross-sectional views showing the operation of the head ball of the clutch mechanism of FIG. 1, in which FIG. 2A shows a non-transmission state and FIG. 3A and 3B are cross-sectional views in a direction crossing the axis of the clutch mechanism of FIG. 2, FIG. 3A shows a non-transmission state, and FIG. 3B shows a transmission state. FIG. 4A is a schematic diagram showing the shape of the first strut of the clutch mechanism of the vehicle in FIG. 1, FIG. 4A is a plan view showing the shape seen from the contact side of the headball and tailball, and FIG. Show. FIG. 5A is a cross-sectional view illustrating the operation of a tail ball of the clutch mechanism of the vehicle in FIG. 1, FIG. 5A illustrates a non-transmission state, and FIG. 5B illustrates a transmission state. 2 is a timing chart showing timings of movement of a head ball and a tail ball of the clutch mechanism of the vehicle in FIG. 1. Sectional drawing of the direction which crosses the axis line at the time of switching from the non-transmission state of the clutch mechanism of the vehicle of FIG. 1 to a transmission state. Sectional drawing which shows the state of the headball at the time of switching from the non-transmission state of the clutch mechanism of the vehicle of FIG. 1 to a transmission state.

  Hereinafter, the driving force transmission device according to the present embodiment will be described with reference to the drawings. This embodiment is an embodiment in which the driving force transmission device of the present invention is used as a clutch mechanism in a vehicle that can be switched between a two-wheel drive state and a four-wheel drive state. However, the driving force transmission device of the present invention is not mounted only on the clutch mechanism of a vehicle, but can be used as various mechanisms in addition to driving force transmission devices such as ships and other vehicles and drones. Is.

  First, a schematic configuration of the vehicle V will be described with reference to FIG.

  As shown in FIG. 1, the vehicle V moves the front wheels of the vehicle V by the case 1, a differential gear DG to which driving force from a driving source (not shown) is transmitted, and the driving force transmitted from the differential gear DG. The driving shaft DS to be driven, the clutch mechanism 2 (driving force transmission mechanism) to which the driving force from the differential gear DG is transmitted, and the driving force transmitted from the clutch mechanism 2 to the rear wheel driving shaft (not shown). And a propeller shaft PS.

  The differential gear DG is rotatably supported on the case 1 by a plurality of first bearings BR1. The clutch mechanism 2 is pivotally supported on the case 1 by a plurality of second bearings BR2. The propeller shaft PS is rotatably supported on the case 1 by a plurality of third bearings BR3.

  On the outer peripheral surface of the differential gear DG, a first ring gear DG1 for transmitting the driving force of the driving source and a second ring gear DG2 for transmitting the driving force from the differential gear DG to the clutch mechanism 2 are provided. .

  Next, the clutch mechanism 2 will be described in detail with reference to FIGS. In FIG. 3, the illustration of the tooth portion of the input gear 20 that meshes with the second ring gear DG2 of the differential gear DG is omitted.

  As shown in FIG. 2, the clutch mechanism 2 includes a ring-shaped input gear 20 (first rotating body) and a cylindrical output shaft that is inserted into the input gear 20 and is rotatable relative to the input gear 20. 21 (second rotating body).

  The input gear 20 meshes with the second ring gear DG2 of the differential gear DG. Therefore, the driving force from the driving source is transmitted to the input gear 20 via the second ring gear DG2.

  As shown in FIG. 3, two first openings 21 a and second openings 21 b communicating with the inside are formed on the peripheral surface of the output shaft 21 so as to be alternately arranged in the circumferential direction.

  A plate-like first strut 22 is disposed in the first opening 21a. A first head ball 23 (first pressing member) and a first tail ball 24 that are movable in the radial direction are arranged inside the first strut 22 in the radial direction.

  As shown in FIG. 4, the first strut 22 includes a pair of first shaft portions 22a extending in an axial direction parallel to the axis of the output shaft 21, a first end portion 22b positioned on one side of the axis, And a first other end 22c located on the other side of the axis.

  The end surface of the first end portion 22b is an engagement end surface 22b1 that engages with a first engagement portion 20a1 of the input gear 20 described later.

  The first head ball 23 corresponds to the portion of the first end 22b that contacts the first head ball 23 (specifically, the portion corresponding to the circle shown by the two-dot chain line on the left side in FIG. 4). Such a depression may be provided. Further, the first tail ball 24 is in contact with the portion of the first other end portion 22c with which the first tail ball 24 abuts (specifically, the portion corresponding to the circle indicated by the two-dot chain line on the right side in FIG. 4). Corresponding depressions may be provided.

  If such a depression is provided, when the first headball 23 and the first tailball 24 come into contact with the first strut 22, the first headball 23 and the first tailball 24 with respect to the first strut 22. Therefore, the pressing force is transmitted to the first strut 22 without waste.

  The first strut 22 is fixed to the output shaft 21 so as to be rotatable about the first shaft portion 22a. Specifically, as shown in FIG. 3, when the first headball 23 moves radially outward (when changing from the state of FIG. 3A to the state of FIG. 3B), the first end portion 22b is pressed by the 1st headball 23, and the 1st strut 22 rotates to one side (FIG. 3 clockwise). As a result, the first end portion 22b protrudes radially outward from the outer peripheral surface of the output shaft 21.

  On the other hand, when the first tail ball 24 moves outward in the radial direction (when changing from the state of FIG. 3B to the state of FIG. 3A), the first other end 22c is pressed against the first tail ball 24. Thus, the first strut 22 rotates to the other side (counterclockwise in FIG. 3). As a result, the first end 22b and the first other end 22c are accommodated in the first opening 21a of the output shaft 21.

  A plate-like second strut 25 is disposed in the second opening 21b. A second head ball 26 (second pressing member) and a second tail ball 27 that are movable in the radial direction are disposed inside the second strut 25 in the radial direction.

  The second strut 25 has the same shape as the first strut 22, a pair of second shaft portions 25 a extending in the axial direction parallel to the axis of the output shaft 21, and a second end positioned on one side of the axis. Part 25b and a second other end 25c located on the other side of the axis.

  The second strut 25 is rotatably fixed to the output shaft 21 around the second shaft portion 25a. Specifically, when the second headball 26 moves outward in the radial direction (when the state changes from the state of FIG. 3A to the state of FIG. 3B), the second end portion 25 b has the second headball 26. The second strut 25 rotates to the other side (counterclockwise in FIG. 3). As a result, the second end portion 25b protrudes radially outward from the outer peripheral surface of the output shaft 21.

  On the other hand, when the second tail ball 27 moves outward in the radial direction (when changing from the state of FIG. 3B to the state of FIG. 3A), the second other end portion 25 c is pressed against the second tail ball 27. Then, the second strut 25 rotates to the other side (clockwise in FIG. 3). As a result, the second end portion 25 b and the second other end portion 25 c are accommodated in the second opening 21 b of the output shaft 21.

  In the clutch mechanism 2, spherical members are used as the first headball 23 and the second headball 26 that are pressing members. This is to reduce the sliding resistance when moving in the radial direction and the impact when contacting the first strut 22 and the second strut 25. However, the shape of the pressing member may be other shapes. For example, a columnar shape extending in the radial direction may be used. However, in the case of such a columnar shape, it is preferable that the end is a spherical surface.

  Moreover, in the clutch mechanism 2, the 1st opening part 21a and the 2nd opening part 21b of the output shaft 21, the 1st strut 22 and the 2nd strut 25 which are arrange | positioned to them, and the 1st headball for pressing them 23, the first tail ball 24, the second head ball 26, and the second tail ball 27 are arranged in a line in the circumferential direction. However, these need only be arranged so as to correspond to a first engaging part 20a1 and a second engaging part 20a2 of the input gear 20 described later, and do not necessarily need to be arranged in a line in the circumferential direction.

  The first head ball 23 and the first tail ball 24 that rotate the first strut 22, and the second head ball 26 and the second tail ball 27 that rotate the second strut 25 are arranged in the radial direction by the cam mechanism 28. Moved to.

  As shown in FIG. 2, the cam mechanism 28 is disposed inside the output shaft 21, is fixed to the case 1, is connected to one end of the cam rod 28 a, and is fixed to the case 1. An actuator ACT, a cylindrical cam ring 28b which is disposed inside the output shaft 21 and through which the cam rod 28a is inserted, a circlip 28c fixed to the outer peripheral surface of the other end of the cam rod 28a, the cam ring 28b and the cir A coil spring 28d (urging member) disposed between the clip 28c and the coil 28c;

  The cam rod 28a is movable in the axial direction with respect to the output shaft 21 by a driving force from an actuator ACT connected to one end. The other end portion of the cam rod 28a is formed thinner than the other portions, and the step portion is a locking portion 28a1.

  The cam ring 28b can move relative to the cam rod 28a in the axial direction. The cam ring 28 b is located on the radially inner side of the first opening 21 a and the second opening 21 b of the output shaft 21. Therefore, the first head ball 23, the first tail ball 24, the second head ball 26, and the second tail ball 27 are in contact with the outer peripheral surface of the cam ring 28b.

  A first cam surface 28b1 is formed on a portion of the outer peripheral surface of the cam ring 28b that contacts the first head ball 23 and the second head ball 26. On the other hand, a second cam surface 28b2 is formed at a portion of the outer peripheral surface of the cam ring 28b that contacts the first tail ball 24 and the second tail ball 27 (see FIG. 5).

  Due to the first cam surface 28b1 and the second cam surface 28b2, when the cam ring 28b moves relative to the output shaft 21 in the axial direction along with the movement of the cam rod 28a, the first head ball 23 and the first tail ball 24, the second headball 26 and the second tailball 27 move in the radial direction.

  The coil spring 28d attaches the cam ring 28b to one side in the axial direction so that the relative position of the cam ring 28b to the cam rod 28a is a predetermined position (specifically, the position locked by the locking portion 28a1 of the cam rod 28a). It is fast.

  In the cam mechanism 28, a coil spring 28d is used as a biasing member that biases the cam ring 28b. However, the urging member is not limited to the coil spring. For example, rubber or the like may be used in addition to a disc spring or wave spring.

  Incidentally, as shown in FIG. 3, the inner peripheral surface of the input gear 20 through which the output shaft 21 is inserted has a number of recesses 20 a corresponding to the first opening 21 a and the second opening 21 b of the output shaft 21. Is formed.

  The edge part of the one side of the recessed part 20a is the 1st engaging part 20a1. The first engagement portion 20a1 includes a first end 22b of the first strut 22 when the first end 22b of the first strut 22 protrudes from the outer peripheral surface of the output shaft 21 (that is, the state shown in FIG. 3B). Engage with. By engaging in this way, the rotation of the input gear 20 in the forward rotation direction is also transmitted to the output shaft 21.

  On the other hand, the other edge of the recess 20a is a second engagement portion 20a2. When the second end portion 25b of the second strut 25 protrudes from the outer peripheral surface of the output shaft 21 (that is, in the state shown in FIG. 3B), the second engagement portion 20a2 has a second end portion 25b of the second strut 25. Engage with. By engaging in this way, the rotation of the input gear 20 in the reverse direction is also transmitted to the output shaft 21.

  Next, the non-transmission state and the transmission state of the clutch mechanism 2 will be described with reference to FIGS. 2, 3, and 5. 2, 3, and 5, FIGS. 2A, 3 </ b> A, and 5 </ b> A show a non-transmission state, and FIGS. 2B, 3 </ b> B, and 5 </ b> B show a transmission state.

  Here, the non-transmission state is a state in which the rotation of the input gear 20 is not transmitted to the output shaft 21 even when the input gear 20 rotates relative to the output shaft 21 in either the reverse rotation direction or the normal rotation direction. The transmission state refers to a state in which the rotation of the input gear 20 is transmitted to the output shaft 21 regardless of which direction the input gear 20 rotates relative to the output shaft 21.

  In the non-transmission state, as shown in FIG. 2A, the first head ball 23 is not pressed against the first cam surface 28b1 of the cam ring 28b of the cam mechanism 28, and is thus movable in the radial direction. . On the other hand, as shown in FIG. 5A, the first tail ball 24 is pressed against the second cam surface 28b2 of the cam ring 28b of the cam mechanism 28, and is fixed at a radially outer position.

  Therefore, as shown in FIG. 3A, the first strut 22 is held in a state where the first end 22 b does not protrude from the outer peripheral surface of the output shaft 21 due to the pressing force applied from the first tailball 24. The first headball 23 is also fixed at a radially inner position by applying a pressing force from the first tailball 24 via the first strut 22.

  Similarly, since the second head ball 26 is not pressed against the first cam surface 28b1 of the cam ring 28b of the cam mechanism 28, the second head ball 26 is movable in the radial direction. On the other hand, the second tail ball 27 is pressed against the second cam surface 28b2 of the cam ring 28b of the cam mechanism 28, and is fixed at a radially outer position.

  Therefore, the second strut 25 is held in a state where the second end portion 25 b does not protrude from the outer peripheral surface of the output shaft 21 by the pressing force applied from the second tail ball 27. The second headball 26 is also fixed at a radially inner position by applying a pressing force from the second tailball 27 via the second strut 25.

  Thus, in the non-transmission state in which the first end 22b of the first strut 22 and the second end 25b of the second strut 25 do not protrude from the outer peripheral surface of the output shaft 21, the input gear 20 and the output shaft 21 Does not engage.

  Therefore, the rotation of the input gear 20 is not transmitted to the output shaft 21, and the input gear 20 and the output shaft 21 are relatively rotatable. At this time, since the driving force is not transmitted to the drive shaft of the rear wheel of the vehicle V, the vehicle V is in a two-wheel drive state.

  On the other hand, in the transmission state, as shown in FIG. 2B, the first headball 23 is pressed against the first cam surface 28b1 of the cam ring 28b of the cam mechanism 28 and is fixed at a radially outer position. On the other hand, as shown in FIG. 5B, since the first tail ball 24 is not pressed against the second cam surface 28b2 of the cam ring 28b of the cam mechanism 28, it is movable in the radial direction.

  Therefore, as shown in FIG. 3B, the first strut 22 is in a state where the first end 22 b protrudes from the outer peripheral surface of the output shaft 21 due to the pressing force applied from the first headball 23. As a result, the first end portion 22b engages with the first engagement portion 20a1 provided on the inner peripheral surface of the input gear 20.

  Similarly, the second head ball 26 is pressed against the first cam surface 28b1 of the cam ring 28b of the cam mechanism 28 and is fixed at a radially outer position. On the other hand, since the second tail ball 27 is not pressed against the second cam surface 28b2 of the cam ring 28b of the cam mechanism 28, the second tail ball 27 is movable in the radial direction.

  Therefore, the second strut 25 is in a state where the second end portion 25 b protrudes from the outer peripheral surface of the output shaft 21 due to the pressing force applied from the second headball 26. The second end portion 25 b engages with a second engagement portion 20 a 2 provided on the inner peripheral surface of the input gear 20.

  Thus, in the transmission state in which the first end 22b of the first strut 22 and the second end 25b of the second strut 25 protrude from the outer peripheral surface of the output shaft 21, the input gear 20 and the output shaft 21 are connected. Engage. That is, the rotation on the forward rotation side of the input gear 20 is transmitted to the output shaft 21 through the engagement between the first end portion 22b and the first engagement portion 20a1. On the other hand, the rotation on the reverse side of the input gear 20 is transmitted to the output shaft 21 through the engagement between the second end portion 25b and the second engagement portion 20a2.

  Therefore, the rotation of the input gear 20 is transmitted to the output shaft 21, and the input gear 20 and the output shaft 21 rotate integrally. That is, since the rotation of the input gear 20 is transmitted to the output shaft 21, the driving force is also transmitted to the drive shaft of the rear wheel of the vehicle V, and the vehicle V enters a four-wheel drive state. Further, since the rotation of the output shaft 21 is limited by the rotation of the input gear 20, the engine brake is effective in the vehicle V.

  Next, operations of the first headball 23, the first tailball 24, the second headball 26, and the second tailball 27 when switching from the non-transmission state to the transmission state will be described with reference to FIGS. To do.

  In the clutch mechanism 2, the first headball 23, the first tailball 24, the second headball 26, and the second tailball 27 are moved in the radial direction at different timings when switching from the non-transmission state to the transmission state. I am letting. That is, the shape of the first cam surface 28b1 and the shape of the second cam surface 28b2 correspond to the first head ball 23, the first tail ball 24, the second head ball 26, and the second tail ball 27 in the circumferential direction. The shape is shifted in the axial direction.

  Specifically, as shown in FIG. 3, first, the first tail ball 24 is located radially inward from the radially outer position by releasing the pressing by the second cam surface 28b2. It can move to the inner position (time t1 in FIG. 6). Thereby, the first strut 22 for transmitting the rotation in the normal rotation direction can be rotated.

  Next, the first head ball 23 starts to move from the inner position to the outer position by being pressed against the first cam surface 28b1 (time t2 in FIG. 6).

  Further, simultaneously with the start of the movement of the first headball 23, the second tailball 27 can be moved from the outer position to the inner position by releasing the pressing by the second cam surface 28b2 (FIG. 6). Time t2). Thereby, the second strut 25 for transmitting the rotation in the reverse direction can be rotated.

  Next, the second head ball 26 starts to move from the inner position to the outer position side by being pressed against the first cam surface 28b1 (time t3 in FIG. 6).

  Next, the first tail ball 24 is pressed by the first other end 22c of the first strut 22 to complete the movement to the inner position (time t4 in FIG. 6).

  Next, the first headball 23 completes moving to the outer position (time t5 in FIG. 6). As a result, the first end 22b of the first strut 22 protrudes from the output shaft 21 and engages with the first engagement portion 20a1 of the input gear 20.

  At the same time as the movement of the first headball 23 is completed, the second tailball 27 is pressed against the second other end 25c of the second strut 25 to complete the movement to the inner position (FIG. 6). Time t5).

  Finally, the second headball 26 completes the movement to the outer position (time t6 in FIG. 6). As a result, the second end 25b of the second strut 25 protrudes from the output shaft 21 and engages with the second engagement portion 20a2 of the input gear 20.

  As described above, when the cam mechanism 28 of the clutch mechanism 2 is switched from the non-transmission state to the transmission state, the first head ball 23 for transmitting the forward driving force is moved to the radially outer position. Then, the second head ball 26 for transmitting the reverse driving force is moved to an outer position located radially outward.

  That is, when the cam mechanism 28 of the clutch mechanism 2 is switched from the non-transmission state to the transmission state, the first strut 22 is engaged with the first engagement portion 20a1 of the input gear 20, and then the direction of the cam mechanism 28 is changed. A different second strut 25 is engaged with the second engagement portion 20 a 2 of the input gear 20.

  Thereby, after the position of the recessed portion 20a of the input gear 20 in which the first engaging portion 20a1 and the second engaging portion 20a2 are formed by the first strut 22, the second strut 25 is engaged. Become.

  Therefore, compared to a configuration in which two types of struts are engaged at the same time, the clearance between the strut and the engagement portion necessary for engagement (that is, the first engagement with the first end 22b of the first strut 22 and the first engagement). And the distance between the second end 25b of the second strut 25 and the second engaging portion 20a2) can be reduced. As a result, smooth engagement is possible without increasing the clearance.

  Therefore, according to the clutch mechanism 2, the driving force can be transmitted regardless of which direction the input gear 20 rotates with respect to the output shaft 21, and can be smoothly engaged and switched to the transmission state. In the transmission state, it is possible to suppress the occurrence of rattling that causes noise and vibration.

  By the way, when it is going to switch from a non-transmission state to a transmission state in the state in which the input gear 20 is rotating relative to the output shaft 21, depending on the switching timing, the first end 22b of the first strut 22 and the first The second end 25b of the two struts 25 may come into contact with a portion other than the recess 20a of the input gear 20, and an unintended load may be applied to the first strut 22 and the second strut 25.

  Therefore, in the clutch mechanism 2, an unintended load is prevented from being applied to the first strut 22 and the second strut 25 by adjusting the movement timing of the cam ring 28b using the coil spring 28d.

  Hereinafter, a mechanism using the coil spring 28d will be described with reference to FIGS. 2, 7, and 8. FIG.

  As shown in FIG. 2A, in the non-transmission state, in the coil spring 28d, the relative position of the cam ring 28b with respect to the cam rod 28a is a predetermined position (specifically, a position locked by the locking portion 28a1 of the cam rod 28a). Thus, the cam ring 28b is urged toward the one side in the axial direction.

  Therefore, when switching from the non-transmission state to the transmission state (that is, when the cam rod 28a is moved in one direction (leftward in FIG. 2A) by the driving force from the actuator ACT), the first strut 22 and the second strut 25 are When it exists in the position corresponding to the recessed part 20a of the input gear 20, the 1st headball 23 and the 2nd headball 26 move to an outer side position. As a result, the movement of the cam ring 28 b is not hindered by the first headball 23 and the second headball 26.

  On the other hand, when switching from the non-transmission state to the transmission state, as shown in FIG. 7, when the first strut 22 and the second strut 25 are not present at the position corresponding to the recess 20a of the input gear 20, The first headball 23 and the second headball 26 abut against the inner peripheral surface of the input gear 20 and are held at the inner position. As a result, the movement of the cam ring 28 b is inhibited by the first headball 23 and the second headball 26.

  At this time, as shown in FIG. 8, the coil spring 28d is in a compressed state, and the cam ring 28b is biased to one side (left side in FIG. 8).

  Therefore, when the input gear 20 rotates relative to the output shaft 21 and the recess 20a of the input gear 20 moves to a position corresponding to the first strut 22 and the second strut 25 (that is, the first headball 23 and the first When the two head balls 26 are movable in the radial direction (see FIG. 3), the first head balls 23 and the second head balls 26 are pressed by the cam ring 28b moved by the biasing force of the coil spring 28d. Thus, it moves to the outer position.

  That is, since the clutch mechanism 2 is provided with the coil spring 28d for urging the cam ring 28b in this way, the first strut 22 and the second strut 25 are recessed in the input gear 20 when switching from the non-transmission state to the transmission state. If it does not exist at the position corresponding to 20a, the driving force transmitted from the actuator ACT to the cam rod 28a is temporarily absorbed by the coil spring 28d.

  Therefore, according to the clutch mechanism 2, an unintended load is hardly applied to the first strut 22 and the second strut 25 regardless of the switching timing.

  Although the illustrated embodiment has been described above, the present invention is not limited to such a form.

  For example, in the above embodiment, the clutch mechanism 2 is configured to insert the output shaft 21 that is the second rotating body into the input gear 20 that is the first rotating body. However, the driving force transmission device of the present invention is not limited to such a configuration, and a configuration for transmitting rotation from the second rotating body inserted into the first rotating body to the first rotating body. It may be.

  In the above embodiment, the clutch mechanism 2 engages the first strut 22 that transmits the rotation on the forward rotation side to the input gear 20 (that is, for changing the two-wheel drive state to the four-wheel drive state). After that, the second strut 25 for transmitting the reverse rotation (that is, for applying the engine brake in the four-wheel drive state) is engaged.

  This is because the clutch mechanism 2 is mounted on the vehicle V, so that the time required to complete the switching from the two-wheel drive state to the four-wheel drive state (responsiveness) is such that the engine brake is effective in the four-wheel drive. This is because priority should be given to the responsiveness until. That is, the strut that transmits the rotation in the preferential direction is engaged prior to the other struts.

  Therefore, when the driving force transmission device of the present invention is mounted on a device other than the vehicle, the strut to be engaged first transmits the rotation in any direction as long as the strut that transmits the rotation to be prioritized is transmitted. It may be.

  In the above-described embodiment, the clutch mechanism 2 is a member that presses the first strut 22 and the second strut 25, in addition to the first headball 23 and the second headball 26 that are pressing members, the first tailball. 24 and a second tail ball 27.

  The first tailball 24 and the second tailball 27 cooperate with the second cam surface 28b2 of the cam ring 28b to disengage the first strut 22, the second strut 25, and the first headball 23. The second headball 26 is held in a predetermined position.

  However, the driving force transmission device of the present invention is not limited to the configuration including the tail ball, and the tail ball may be omitted. When the tail ball is omitted, it is preferable to provide a mechanism for controlling the position of the head ball in the radial direction. For example, the cam ring may be formed of a magnet, and the headball and the strut may be formed of a magnetic material.

DESCRIPTION OF SYMBOLS 1 ... Case, 2 ... Clutch mechanism (driving force transmission device), 20 ... Input gear (1st rotary body), 20a ... Recessed part, 20a1 ... 1st engaging part, 20a2 ... 2nd engaging part, 21 ... Output shaft (Second rotating body), 21a ... first opening, 21b ... second opening, 22 ... first strut, 22a ... first shaft, 22b ... first end, 22b1 ... engagement end face, 22c ... first 1 other end, 23 ... first head ball (first pressing member), 24 ... first tail ball, 25 ... second strut, 25a ... second shaft, 25b ... second end, 25c ... second others End part 26 ... second head ball (second pressing member) 27 ... second tail ball 28 ... cam mechanism 28a ... cam rod 28a1 locking part 28b cam ring 28b1 first cam surface 28b2 ... Second cam surface, 28c ... Circlip, 28d ... Coil NE (biasing member), ACT ... actuator, BR1 ... first bearing, BR2 ... second bearing, BR3 ... third bearing, DG ... differential gear, DG1 ... first ring gear, DG2 ... second ring gear, DS ... drive shaft , PS ... propeller shaft, V ... vehicle.

Claims (2)

A cylindrical first rotating body;
A cylindrical second rotator inserted into the first rotator, rotatable relative to the first rotator, and having a first opening and a second opening on a circumferential surface;
A first strut disposed in the first opening and rotatably fixed to the second rotating body about an axis extending in the axial direction of the second rotating body;
The first strut is disposed on the radially inner side of the first strut and is movable in the radial direction. When the first strut moves outward in the radial direction, the first strut is pressed to rotate the first strut. A first pressing member that moves one end portion radially outward;
A second strut disposed in the second opening and fixed to the second rotating body so as to be rotatable about an axis extending in the axial direction of the second rotating body;
The second strut is disposed on the radially inner side of the second strut and is movable in the radial direction. When the second strut moves outward in the radial direction, the second strut is rotated by pressing one end of the second strut. A second pressing member that moves one end portion radially outward;
A cam mechanism for moving the first pressing member and the second pressing member in a radial direction;
The first rotating body is formed on an inner peripheral surface of the first rotating body, and engages with the one end portion when the one end portion of the first strut moves radially outward, so that the first rotating body is engaged with the first rotating body. And a first engaging portion for integrally rotating the second rotating body to one side and an inner peripheral surface of the first rotating body, and one end portion of the second strut moves radially outward. A second engaging portion that engages with the one end portion and rotates the first rotating body and the second rotating body integrally to the other side,
The cam mechanism is in a transmission state in which one end of the first strut and the first engaging portion are engaged and the one end of the second strut and the second engaging portion are engaged. In this case, the first pressing member is moved radially outward, and then the second pressing member is moved radially outward. The driving force transmission device according to claim 1,
The cam mechanism is disposed coaxially with the second rotator inside the second rotator, and is movable in the axial direction with respect to the second rotator; an actuator that moves the cam rod; A cylindrical cam ring inserted through the cam rod and movable relative to the cam rod in the axial direction, and fixed to the cam rod, the cam ring is moved in the axial direction so that the relative position of the cam ring with respect to the cam rod is a predetermined position. A biasing member for biasing,
A cam surface is formed on the outer peripheral surface of the cam ring to move the first pressing member and the second pressing member radially outward when the cam ring moves to a position corresponding to the transmission state. A driving force transmission device characterized by the above.