JP6090211B2 - Clutch device - Google Patents

Description

  The present invention relates to a clutch device. In particular, the present invention relates to an improvement in a clutch device that switches the connected state of both of them by moving the driven side rotating body forward and backward relative to the driving side rotating body.

  2. Description of the Related Art Conventionally, a clutch device that switches between an engaged state where engine power is transmitted to a water pump and a released state where engine power is not transmitted is known. For example, Patent Document 1 includes a driving-side rotator linked to a crankshaft and a driven-side rotator linked to a water pump, and these rotators are pressed together by using magnetic force. A clutch device that is in a combined state is disclosed. Specifically, the clutch device disclosed in Patent Document 1 includes a magnet that applies a magnetic force directed to the driving side rotating body to the driven side rotating body, and a coil that cancels the magnetic field of the magnet when energized. I have. When the coil is not energized, the driving-side rotator and the driven-side rotator are brought into press-contact with each other by the magnetic force of the magnet to be engaged. Thereby, power is transmitted to the water pump. On the other hand, when the coil is energized, the magnetic field of the magnet is canceled by the magnetic field generated around the coil, and the driving side rotating body and the driven side rotating body are separated from each other to be released. As a result, power is not transmitted to the water pump.

  However, in the configuration of Patent Document 1, when the torque to be transmitted to the water pump is large, it is necessary to increase the pressure contact force for pressing the rotating bodies. In this case, it is necessary to enlarge the magnet. The coil for canceling the magnetic field of the large magnet (for switching from the engaged state to the released state) also needs to be enlarged. For this reason, it is difficult for the configuration of Patent Document 1 to reduce the size of the entire clutch device.

  Therefore, the applicant of the present patent application has applied for a clutch device that enables switching from the engaged state to the released state using the rotational force of the driven-side rotator (Japanese Patent Application No. 2012-211046 and Japanese Patent Application No. 2002-11046). 2013-154986).

  Specifically, the driven side rotator is movable forward and backward with respect to the drive side rotator. Further, an urging means for applying an urging force directed to the driving side rotating body to the driven side rotating body is provided. In addition, an inclined groove and a linear groove are provided adjacent to each other on the outer peripheral surface of the driven side rotating body, and a locking member that can be inserted into the inclined groove is provided. In a state where the locking member is not inserted into the inclined groove, the driven side rotator moves forward toward the driving side rotator by the urging force of the urging means, and these rotators are connected to each other to engage the clutch. The device is engaged. On the other hand, when the locking member is inserted into the inclined groove, the rotational force of the driven-side rotator is changed to the force that slides the driven-side rotator due to the contact between the locking member and the side surface of the inclined groove. Converted. As a result, the driven side rotator rotates while moving backward from the drive side rotator, and the rotators are separated from each other to release the clutch device. Then, when the rotation of the driven-side rotating body further proceeds and the locking member moves from the inclined groove to the linear groove, the locking member and the side surface of the linear groove come into contact with each other. Thereby, the released state of the clutch device is maintained by restricting the forward / backward movement of the driven-side rotating body.

JP 2010-203406 A

  The inventor of the present invention considered further improvements for enhancing the practicality of the clutch device according to the application. Then, when the side surface of the inclined groove is brought into contact with the locking member, it has been noted that the contact load (impact load) generated between the both needs to be reduced. Hereinafter, the situation where the contact load increases in the clutch device according to the application will be described.

  The clutch device changes from the engaged state to the released state when the rotational speed of the water pump is controlled to the deceleration side or when the water pump is stopped. That is, the locking member moves forward toward the inclined groove of the driven-side rotator in response to the clutch release request (for example, the locking member rotates toward the driven-side rotator). Inserted into. For this reason, the timing at which the locking member starts moving forward toward the inclined groove of the driven-side rotator is determined regardless of the rotational position of the driven-side rotator.

  In general, when the locking member is inserted into the inclined groove of the driven rotating body rotating in the engaged state of the clutch device, a slight gap is formed between the locking member and the side surface of the inclined groove. (Gap in the direction along the rotation axis) is generated. Then, the side of the inclined groove approaches the engaging member as the rotation of the driven side rotating body progresses from the time when the engaging member is inserted into the inclined groove, and the driven side described above after the two come into contact with each other The retreating movement of the rotating body (retreating movement from the driving side rotating body) is started.

  However, as described above, the timing at which the locking member starts to advance toward the inclined groove is not controlled according to the rotational position of the driven-side rotating body. In the middle of the operation of inserting the locking member into the inclined groove (in a state where the insertion operation is not completed), the side surface of the inclined groove may come into contact with the locking member. For example, when the locking member starts moving forward toward the inclined groove, the side surface of the inclined groove is already approaching the location where the locking member is inserted. In such a situation, there is a possibility that the side surface of the inclined groove contacts the locking member in a state where the amount of the locking member inserted into the inclined groove is small (the insertion depth is shallow). FIG. 16 is a diagram illustrating a state in which the side surface b1 of the inclined groove b is in contact with the locking member a at such timing (viewed from a direction along the axis of the driven-side rotating body c). FIG. 17 is a development view of the inclined groove b in a state where the side surface b1 of the inclined groove b contacts the locking member a at such timing.

  As described above, when the side surface b1 of the inclined groove b comes into contact with the locking member a in a state where the amount of the locking member a inserted into the inclined groove b is small, the locking is performed at the time when the contact is started. Only the tip portion of the member a receives a contact load from the side surface b1 of the inclined groove b. For this reason, the contact load which acts on the front-end | tip part of this latching member a will become extremely large.

  If a situation where such a large contact load acts frequently appears, a part of the locking member (tip portion) will be worn down, which will adversely affect the releasing operation of the clutch device, and the long life of the locking member. There is a possibility of adversely affecting the conversion. Moreover, a part of the side surface of the inclined groove may be worn by this contact load.

  For this reason, the timing at which the locking member is inserted into the inclined groove is set to a timing at which the contact load does not increase, thereby improving the reliability of the operation of the clutch device and the components of the clutch device. The inventors of the present invention have considered that it is necessary to extend the life.

  In order to control the timing at which the locking member is inserted into the inclined groove, it is conceivable to provide an angle sensor for detecting the rotational position of the driven side rotating body. However, this is not preferable because it causes an increase in cost.

  The present invention has been made in view of such points, and the object of the present invention is to define the timing at which the locking member is inserted into the inclined groove without the need to detect the rotational position of the driven-side rotating body. Then, it is providing the clutch apparatus which can relieve the contact load at the time of the side surface of an inclination groove | channel contacting a locking member.

-Solution principle of the invention-
The solution principle of the present invention devised to achieve the above object provides a restricting member that can restrict the insertion of the locking member into the inclined groove. In addition, the restricting member is rotated in synchronization with the driven-side rotating body, whereby the insertion of the locking member into the inclined groove is restricted according to the rotation position of the restricting member, and the insertion is allowed. Change state. Accordingly, the position where the locking member is inserted into the inclined groove can be optimized.

-Solution-
Specifically, the present invention is movable between a connection position connected to the drive-side rotating body and a connection release position where the connection is released, and on the one side in the axial direction with respect to the circumferential direction. A driven-side rotating body including an inclined groove having an inclined side surface inclined so as to be directed, and a linear groove having a side surface provided adjacent to the inclined groove and extending in a direction orthogonal to the axial direction; A locking member that can be inserted into the inclined groove of the driven-side rotating body, and the driven-side rotating body is rotated at the coupling position in the inclined groove of the driven-side rotating body. When the locking member is inserted, the inclined side surface of the inclined groove comes into contact with the locking member, so that the driven-side rotating body moves toward the connection release position along with the rotation, and The locking member moves from the inclined groove to the straight groove and the connection is released. Target clutch device. With respect to the clutch device, a regulating member that is rotatable in synchronization with the rotation of the driven-side rotating body and has an outer surface with an unequal length from the rotation axis is provided on the driven-side rotating body. Provided on the outer peripheral side of the inclined groove. Then, when the locking member faces a preset insertion restriction request region in the forming range of the inclined side surface in the inclined groove, interference with a long distance from the rotation axis in the restricting member. While the outer surface interferes with the locking member, the insertion of the locking member into the inclined groove is restricted, while the area outside the molding range of the inclined side surface in the inclined groove is set in advance. When the locking member faces the required insertion region, a non-interfering outer surface having a short distance from the rotation axis of the regulating member faces the locking member and interferes with the locking member. Instead, the insertion of the locking member into the inclined groove is allowed.

  Due to this specific matter, when the locking member faces the insertion restriction request area of the inclined groove, the interference outer surface having a long distance from the rotation axis in the restricting member interferes with the locking member. The insertion of the locking member into is restricted. On the other hand, when the locking member faces the insertion required area of the inclined groove, the non-interfering outer surface having a short distance from the rotation axis of the regulating member faces the locking member, so that the locking member The interference member is allowed to be inserted into the inclined groove without interference.

  As the insertion restriction request area, for example, when the locking member starts to advance toward the inclined groove, the movement of the inclined side surface of the inclined groove toward the portion where the locking member is inserted has already started. It is the area that is. By restricting the insertion of the locking member into the insertion restriction request region, the inclined member has the inclined side surface of the inclined groove in a state where the amount of the locking member inserted into the inclined groove is small (the insertion depth is shallow). Contact is avoided.

  In addition, as the insertion request area, for example, when the locking member starts moving toward the inclined groove, the inclined side surface of the inclined groove is still moved toward the position where the locking member is inserted. It is an area that has not started. By allowing the locking member to be inserted only into the insertion request region, the inclined member has an inclined side surface of the inclined groove in a state where the amount of the locking member inserted into the inclined groove is large (the insertion depth is deep). Will come into contact.

  By defining the region where the locking member can be inserted into the inclined groove as described above, the contact load acting on the distal end portion of the locking member can be reduced, the wear of the locking member and the inclination of the inclined groove. Side wear can be suppressed. For this reason, it becomes possible to improve the reliability of the operation of the clutch device and extend the life of each member constituting the clutch device.

  In the present invention, when the locking member faces the insertion restriction request area of the inclined groove, the restriction member restricts the insertion of the locking member into the inclined groove. For this reason, the insertion position of the locking member with respect to the inclined groove can be optimized, and the contact load acting on the locking member can be reduced.

It is sectional drawing of the clutch apparatus which concerns on 1st Embodiment. It is a perspective view of a driven side rotating body. It is a side view which shows the latching member and driven side rotary body in the engagement state of a clutch apparatus. It is a side view which shows the latching member and driven side rotary body in the releasing state of a clutch apparatus. It is a figure which expand | deploys and shows each of the inclined groove formation area and linear groove formation area of a to-be-driven side rotary body. FIG. 5 is a cross-sectional view at a position corresponding to a VI-VI line in FIG. 4 in a state in which the pin of the locking member is inserted into the inclined groove. It is a figure for demonstrating operation | movement of the pin insertion limitation mechanism which concerns on 1st Embodiment, Comprising: It is a side view which shows the pin insertion limitation mechanism and driven side rotary body in the engagement state of a clutch apparatus. It is a figure for demonstrating operation | movement of the pin insertion restriction mechanism which concerns on 1st Embodiment, Comprising: It is a side view which shows the pin insertion restriction mechanism and driven side rotary body in the releasing state of a clutch apparatus. It is a figure which shows the state in which insertion of the pin to an inclination groove is restrict | limited by the pin insertion restriction mechanism in 1st Embodiment. It is a figure which shows the state in which insertion of the pin to an inclined groove is permitted by the pin insertion restriction mechanism in 1st Embodiment. FIG. 6 is a diagram showing an expanded inclined groove forming area of a driven-side rotating body, and a diagram for explaining the relationship among a pin insertion restriction request area, a pin insertion request area, a rotational position of an eccentric cam, and a sliding position of the rotating body. is there. It is a figure for demonstrating operation | movement of the pin insertion limitation mechanism which concerns on 2nd Embodiment, Comprising: It is a side view which shows the pin insertion limitation mechanism and driven side rotary body in the engagement state of a clutch apparatus. It is a figure for demonstrating operation | movement of the pin insertion restriction mechanism which concerns on 2nd Embodiment, Comprising: It is a side view which shows the pin insertion restriction mechanism and driven side rotary body in the releasing state of a clutch apparatus. It is a figure which shows the state in which insertion of the pin to an inclination groove is restrict | limited by the pin insertion restriction mechanism in 2nd Embodiment. It is a figure which shows the state in which insertion of the pin to an inclined groove is permitted by the pin insertion restriction mechanism in 2nd Embodiment. It is the figure which looked at the state where there is little insertion amount of the latching member with respect to an inclination groove | channel from the direction along the axis of the driven side rotary body. It is an expanded view of the inclination groove | channel which shows the state which the side surface of the inclination groove contacted the engagement member in the state where there is little insertion amount of the engagement member with respect to an inclination groove | channel.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. This embodiment demonstrates the case where the clutch apparatus based on this invention is applied to the water pump with which the cooling system of the engine (internal combustion engine) for motor vehicles was equipped. That is, it is a clutch device provided in a power transmission system that transmits power from the engine to the water pump, and switches between a state (engaged state) in which the engine power is transmitted to the water pump and a state in which it is not transmitted (released state). It will be explained as a thing.

  FIG. 1 is a cross-sectional view of the clutch device 1 according to the present embodiment. In FIG. 1, components for transmitting engine power to the clutch device 1 and main components of the water pump 8 are indicated by phantom lines.

  As shown in FIG. 1, the clutch device 1 includes a clutch housing 2 and a clutch mechanism 3 disposed in an inner space of the clutch housing 2.

(Clutch housing and clutch output shaft)
The clutch housing 2 is fixed to, for example, a cylinder block (not shown) of the engine, and has a flat plate-like base portion 21 extending in the vertical direction and a surface on one side of the base portion 21 (the left surface in the drawing). And a substantially cylindrical clutch mechanism accommodating portion 22 formed. The clutch mechanism 3 is disposed in the inner space of the clutch mechanism housing portion 22.

  A through hole 23 penetrating in the horizontal direction is formed at the center of the base portion 21 of the clutch housing 2. A substantially cylindrical support member 24 is fitted into the through hole 23. The support member 24 rotatably supports the clutch output shaft 11 via a first bearing B1 disposed on the inside thereof.

  An impeller 81 of the water pump 8 is attached to the front end side (right end side in FIG. 1) of the clutch output shaft 11 so as to be integrally rotatable.

  On the other hand, on the base end side (left end side in FIG. 1) of the clutch output shaft 11, a driving side rotating body 4 and a driven side rotating body 5 constituting the clutch mechanism 3 are provided. As for the arrangement positions of the driving side rotating body 4 and the driven side rotating body 5, the driven side rotating body 5 is closer to the water pump than the driving side rotating body 4. The drive side rotator 4 is supported on the clutch output shaft 11 via the second bearing B2 so as to be relatively rotatable. The driven-side rotating body 5 is supported on the clutch output shaft 11 by spline fitting so as to be able to rotate integrally and move along the axial direction. The configurations of the driving side rotating body 4 and the driven side rotating body 5 will be described later.

(Clutch mechanism)
The clutch mechanism 3 is configured by a so-called ball lock type clutch mechanism, and includes the driving side rotating body 4 and the driven side rotating body 5. The clutch mechanism 3 establishes an engaged state of the clutch device 1 by connecting the driving side rotating body 4 and the driven side rotating body 5, thereby operating the water pump 8. Further, the clutch mechanism 3 establishes the released state of the clutch device 1 by releasing the connection between the driving side rotating body 4 and the driven side rotating body 5, thereby stopping or decelerating the water pump 8. For example, the rotational speed of the water pump 8 can be arbitrarily adjusted by adjusting the ratio of the period during which the clutch device 1 is engaged and the period during which the clutch device 1 is released within a predetermined period. Hereinafter, the configuration of the driving side rotating body 4 and the driven side rotating body 5 will be specifically described.

  The driving side rotating body 4 is connected to the driven side pulley 71 so as to be integrally rotatable by means such as bolting. The driven pulley 71 has a shape surrounding the outer peripheral side of the clutch mechanism 3 and the outer peripheral side of the clutch mechanism accommodating portion 22 of the clutch housing 2. The driven pulley 71 is rotatably supported by the clutch housing 2 via the third bearing B3. On the other hand, a driving pulley 73 is connected to the end of the crankshaft 72 of the engine (power generation source) so as to be integrally rotatable. Auxiliary machine belt 74 is stretched over driven pulley 71 and drive pulley 73. As a result, the rotational force of the crankshaft 72 is transmitted to the driven pulley 71 via the driving pulley 73 and the accessory belt 74. When the driven pulley 71 rotates due to the transmission of this rotational force, the driving side rotating body 4 also rotates accordingly.

  As shown in FIG. 2 (a perspective view of the driven-side rotator 5), the driven-side rotator 5 includes a large-diameter portion 51 and a small-diameter portion 52 having different outer diameter dimensions. The large-diameter portion 51 is located on the drive side rotating body 4 side (left side in FIG. 1) in the axial direction. The small diameter portion 52 is located on the water pump 8 side (right side in FIG. 1) in the axial direction.

  The small-diameter portion 52 of the driven-side rotator 5 is formed with a recess 52a (see FIG. 1) that opens toward the water pump 8 side. The inner diameter dimension of the recess 52a is set slightly larger than the outer diameter dimension of the support member 24, and a part of the support member 24 is inserted into the recess 52a.

  An accommodation recess 52b for accommodating the biasing member SP is formed at the bottom of the recess 52a. The accommodating recesses 52b are provided at a plurality of locations in the circumferential direction on the outer peripheral side of the clutch output shaft 11.

  The urging member SP is made of, for example, a coil spring. On the outer peripheral surface of the clutch output shaft 11, a flange-shaped locking projection 11a facing the housing recess 52b is provided. The urging member SP is disposed in a compressed state between the locking protrusion 11a and the housing recess 52b of the driven side rotating body 5. As a result, the driven-side rotator 5 is biased toward the drive-side rotator 4 (toward the left side in FIG. 1).

  The drive-side rotator 4 is provided with a recess 41 that opens toward the driven-side rotator 5 side. The inner diameter of the concave portion 41 is larger than the large diameter portion 51 of the driven-side rotator 5, and the large-diameter portion 51 of the driven-side rotator 5 is inserted into the concave portion 41. Thereby, the outer peripheral surface of the large-diameter portion 51 of the driven-side rotator 5 and the inner peripheral surface of the concave portion 41 of the drive-side rotator 4 face each other in the radial direction.

  The large-diameter portion 51 of the driven-side rotator 5 is provided with a plurality of (for example, three) extension portions 51a, 51a, 51a extending toward the concave portion 41 of the driving-side rotator 4. These extension parts 51a, 51a, 51a are provided at positions at equal intervals in the circumferential direction of the large diameter part 51, as shown in FIG.

  Spherical housing grooves 53 are respectively formed on the outer peripheral surfaces of the extension portions 51a, 51a, 51a. The spherical body accommodation groove 53 includes a connection release groove portion 54 and a connection groove portion 55. The connection release groove portion 54 extends along the axial direction of the driven side rotating body 5. The connecting groove portion 55 extends along the circumferential direction of the driven-side rotating body 5 from one end (one end near the small diameter portion 52) of the connection releasing groove portion 54. The extension direction of the connection groove 55 from one end of the connection release groove 54 is the direction toward the downstream side of the rotation direction of the drive side rotating body 4 when receiving the rotational force from the crankshaft 72 (the tip of the clutch output shaft 11). (The clockwise direction when the driving side rotating body 4 is viewed from the right side in FIG. 1).

  As the depth dimension of the spherical body accommodation groove 53, the connection release groove part 54 is the deepest and the connection groove part 55 is the shallowest. The depth dimension gradually becomes shallower from the connection release groove portion 54 toward the connection groove portion 55.

  On the other hand, an arc groove 42 is formed on the inner peripheral surface of the concave portion 41 of the drive side rotating body 4 over the entire periphery thereof. As shown in FIG. 1, the arc groove 42 has a substantially arc shape in cross section. The depth dimension of the arc groove 42 is substantially the same over the entire circumference of the drive side rotating body 4. Thereby, the circular arc groove 42 of the driving side rotating body 4 and the spherical body accommodation groove 53 of the driven side rotating body 5 face each other. The sphere 31 is accommodated in the space formed by the arc groove 42 and the sphere accommodating groove 53 (see FIGS. 1, 3, and 4).

  As described above, the driven-side rotator 5 is movable along the axial direction of the clutch output shaft 11. That is, the driven-side rotator 5 is axially positioned between a position approaching the drive-side rotator 4 (position shown in FIG. 3) and a position retreating from the drive-side rotator 4 (position shown in FIG. 4). It is possible to move forward and backward (slide movement) along.

  As shown in FIG. 3 (a side view showing the engaged state of the clutch device 1), when the driven side rotating body 5 is moved to a position approaching the driving side rotating body 4 by the biasing force of the biasing member SP. The arc groove 42 of the driving side rotating body 4 and the connecting groove portion 55 of the driven side rotating body 5 face each other. As described above, the depth of the connecting groove 55 is shallow. Specifically, the distance dimension between the inner peripheral surface of the concave portion 41 of the driving side rotating body 4 and the outer peripheral surface of the large diameter portion 51 of the driven side rotating body 5, the depth dimension of the connecting groove portion 55, and the arc groove The sum total with the depth dimension of 42 is slightly smaller than the outer diameter dimension of the sphere 31. Therefore, as shown in FIG. 3, when the sphere 31 is positioned in the vicinity of the connecting groove 55, the sphere 31 cannot be rotated by being sandwiched between the connecting groove 55 and the arc groove 42. . That is, the sphere 31 is fitted between the connecting groove 55 and the arc groove 42 so as not to rotate, whereby the rotational force of the drive side rotator 4 is transmitted to the driven side rotator 5 via the sphere 31. Will be. That is, the driving side rotating body 4 and the driven side rotating body 5 are connected. In this case, the clutch output shaft 11 and the impeller 81 of the water pump 8 also rotate with the rotation of the driven-side rotating body 5, and cooling water is discharged from the water pump 8. Hereinafter, the position (sliding movement position along the axis) of the driven-side rotating body 5 in a state where the driving-side rotating body 4 and the driven-side rotating body 5 are connected is referred to as the lock position (the connection in the present invention). (Position).

  On the other hand, as shown in FIG. 4 (a side view showing the released state of the clutch device 1), the driven-side rotator 5 is moved back from the driving-side rotator 4 against the urging force of the urging member SP. When moved, the arc groove 42 of the driving side rotating body 4 and the connection releasing groove portion 54 of the driven side rotating body 5 face each other. As described above, the depth of the connection release groove 54 is deep. Specifically, the distance between the inner peripheral surface of the concave portion 41 of the driving-side rotating body 4 and the outer peripheral surface of the large-diameter portion 51 of the driven-side rotating body 5, the depth of the connection release groove 54, and the arc The sum total with the depth dimension of the groove 42 is slightly larger than the outer diameter dimension of the sphere 31. Therefore, when the sphere 31 is positioned in the connection release groove 54 as shown in FIG. 4, there is a gap that allows rotation (idling) of the sphere 31 between the connection release groove 54 and the arc groove 42. It is formed. In this case, even if the driving side rotating body 4 rotates by receiving the rotating force from the crankshaft 72, the transmission of the rotating force to the driven side rotating body 5 by the sphere 31 is not performed. That is, the connection between the driving side rotating body 4 and the driven side rotating body 5 is released. In this case, since the rotational force is not transmitted to the clutch output shaft 11 and the impeller 81 of the water pump 8, the water pump 8 is stopped or decelerated. In the following, the position of the driven side rotating body 5 (sliding movement position along the axis) in a state where the connection between the driving side rotating body 4 and the driven side rotating body 5 is released is the unlock position (the present invention). This is called a connection release position.

  As described above, the connected state and the disconnected state of the driving side rotating body 4 and the driven side rotating body 5 are realized by a mechanism for moving the driven side rotating body 5 forward and backward toward the driving side rotating body 4. That is, the driven-side rotating body 4 and the driven-side rotating body 5 are connected to each other (the engaged state of the clutch device 1) by moving the driven-side rotating body 5 forward toward the driving-side rotating body 4 to the locked position. ) On the other hand, the driven-side rotator 4 and the driven-side rotator 5 are disengaged by releasing the driven-side rotator 5 from the driving-side rotator 4 to the unlock position (the clutch device 1 is released). It becomes.

  Hereinafter, a mechanism (advance / retreat mechanism) for moving the driven-side rotator 5 forward / backward will be described.

(Advance and retreat mechanism)
As shown in FIGS. 3 and 4, the forward / backward moving mechanism 32 includes a groove 56 formed on the outer peripheral surface of the driven-side rotating body 5 and a locking unit having a locking member 61 inserted into the groove 56. 6 is provided. This will be specifically described below.

  The groove 56 extending in the circumferential direction is formed at a position close to the large diameter portion 51 on the outer peripheral surface of the small diameter portion 52 of the driven side rotating body 5. The groove 56 has an inclined groove 57 having an inclined side surface 57aII (see FIG. 5) inclined by a predetermined angle so as to be directed to one side of the axial direction with respect to the circumferential direction (direction orthogonal to the axial direction). And a straight groove 58 having a side surface 58a extending in a direction orthogonal to the axial direction. As the arrangement positions of the inclined grooves 57 and the linear grooves 58, the linear grooves 58 are closer to the large-diameter portion 51 than the inclined grooves 57 are.

  The inclined groove 57 includes a radially extending side surface 57a (a pin insertion side surface 57aI described later and an inclined side surface 57aII that is inclined (inclined by a predetermined angle with respect to the circumferential direction); see FIG. 5). A bottom surface 57b extending in the direction along the axial center from the inner peripheral end of the side surface 57a toward the linear groove 58 side.

  FIG. 5 shows a region where the inclined groove 57 is formed in the small diameter portion 52 of the driven-side rotating body 5 (hereinafter referred to as an inclined groove forming region) and a region where the linear groove 58 is formed (hereinafter referred to as linear groove formation). It is a figure which expands and shows each (it is called an area | region). In FIG. 5, the left-right direction is the circumferential direction of the small-diameter portion 52, and the up-down direction is the direction along the axis of the small-diameter portion 52. As shown in FIG. 5, an inclined groove forming region and a linear groove forming region extending in the circumferential direction are provided adjacent to the outer peripheral surface of the small diameter portion 52, respectively.

  The predetermined range in the circumferential direction of the side surface 57a in the inclined groove forming region is the rotational direction of the driving side rotating body 4 (because it is also the rotating direction of the driven side rotating body 5 when the clutch device 1 is in the engaged state. In the following, gradually approaching the drive-side rotator 4 (sometimes referred to as the rotational direction of the driven-side rotator 5) (toward the right direction in FIG. 5) (to the linear groove 58 gradually). The inclined side surface 57aII is inclined (to approach). The inclination angle and the inclination range of the inclined side surface 57aII (the angular range in the circumferential direction where the inclined side surface 57aII is provided) are necessary for the entire peripheral length of the small diameter portion 52 of the driven side rotating body 5 and the driven side rotating body 5. Is appropriately set according to the amount of movement (the amount of movement between the locked position and the unlocked position). For example, the movement amount (dimension t1 in the figure) between the lock position and the unlock position is 2.0 mm, and the inclination angle (angle α in the figure) of the inclined side surface 57aII is set to 3 °. . Further, the angular range (range t2 in the figure) in the circumferential direction of the region where the inclined side surface 57aII is provided is set to a range of 250 °. These values are not limited to this.

  Thus, since the inclined side surface 57aII inclined with respect to the circumferential direction is formed, the width dimension (the dimension in the direction along the axis) of the bottom surface 57b is within the range t2 where the inclined side surface 57aII is provided. ) Gradually narrows in the circumferential direction (toward the upstream side in the rotational direction of the driven-side rotating body 5).

  Further, on the downstream side (left side in FIG. 5) in the rotational direction of the driven-side rotator 5 with respect to the inclined side surface 57aII, the pin insertion side surface 57aI extending (not inclined) in a direction orthogonal to the axial direction. Is provided. In the range t3 where the pin insertion side surface 57aI is provided, the width dimension (dimension in the direction along the axis) of the bottom surface 57b is uniform over the circumferential direction.

  Further, the inclined groove 57 is not formed on the upstream side (the right side in FIG. 5) in the rotational direction of the driven-side rotating body 5 with respect to the inclined side surface 57aII, and this region corresponds to the outer peripheral surface of the small diameter portion 52. It is a circular arc surface 57aIII that is flush with the outer peripheral surface of the small-diameter portion 52 (the radial dimension is the same).

  The portion where the pin insertion side surface 57aI is provided corresponds to an insertion start region when the pin 69 provided in the locking member 61 of the locking unit 6 is inserted into the inclined groove 57. Hereinafter, this region is referred to as a start end portion 57c. In the inclined groove 57 having the shape shown in FIG. 5, the range t3 in the above-described figure is the formation range of the pin insertion side surface 57aI constituting the start end portion 57c. Further, the upstream end portion of the inclined side surface 57aII in the rotational direction of the driven-side rotating body 5 corresponds to an insertion start position when the pin 69 is detached from the inclined groove 57 and inserted into the linear groove 58. Hereinafter, this portion is referred to as a termination portion 57d.

  Further, as the depth dimension of the inclined groove 57, in the formation range t3 of the pin insertion side surface 57aI, it gradually becomes deeper toward the formation range t2 of the inclined side surface 57aII. Further, in the formation range t2 of the inclined side surface 57aII, the depth dimension of the inclined groove 57 is constant over the entire circumference (FIG. 6 (cross-section at the position corresponding to the VI-VI line in FIG. 4). (See the depth of the inclined groove 57 shown in the figure)).

  On the other hand, the linear groove 58 is formed over the entire circumference of the outer peripheral surface of the driven-side rotating body 5 and adjacent to the inclined groove 57. The linear groove 58 includes the side surface 58a extending in the radial direction and a bottom surface 58b extending in the direction along the axial center from the inner peripheral end of the side surface 58a toward the large diameter portion 51. The entire side surface 58a of the linear groove 58 is a plane orthogonal to the axis. That is, the side surface 58a is not inclined. Further, the bottom surface 58 b of the linear groove 58 is located on the inner peripheral side with respect to the bottom surface 57 b of the inclined groove 57. That is, the depth dimension of the linear groove 58 is larger than the depth dimension of the inclined groove 57. For this reason, the linear groove 58 and the inclined groove 57 are adjacent to each other in a state where a step exists between them. Further, in this linear groove 58, a position adjacent to the terminal end portion 57d of the inclined groove 57 is a start end portion 58c where the insertion of the pin 69 is started.

  As described above, the inclined groove 57 and the linear groove 58 are formed, so that the driven side rotating body 5 is in the locked position as shown in FIG. 3, and the driving side rotating body 4 and the driven side rotating body 5 are located. When the locking member 61 is rotated toward the groove 56, the pin 69 of the locking member 61 is connected to the start end portion 57c of the inclined groove 57 (the pin insertion side surface 57aI is formed). Is inserted into the inclined groove 57 (details of the operation of inserting the pin 69 into the inclined groove 57 will be described later). When the pin 69 is inserted into the inclined groove 57 in this way, the driven-side rotating body 5 rotates with the inclined side surface 57aII of the inclined groove 57 in contact with the pin 69. Then, while the inclined side surface 57aII of the inclined groove 57 slides on the pin 69, the rotational force of the driven side rotating body 5 is converted into a force that causes the driven side rotating body 5 to slide, and this driven side The rotating body 5 moves from the lock position to the unlock position in a direction along the axis (right direction in FIG. 3). With the movement of the driven side rotating body 5, the sphere 31 moves relatively from the connecting groove portion 55 provided in the driven side rotating body 5 toward the connection releasing groove portion 54.

  When the pin 69 reaches the terminal end 57 d of the inclined groove 57, the pin 69 is inserted into the linear groove 58 from the start end 58 c of the linear groove 58. That is, the pin 69 is detached from the inclined groove 57 and fitted into the linear groove 58. As a result, the driven-side rotator 5 is completely moved from the locked position to the unlocked position. Accordingly, the sphere 31 is fitted into the connection release groove 54. Thus, in the clutch device 1, the pin 69 of the locking member 61 is inserted into the groove 56, and the pin 69 is engaged with the inclined side surface 57 a II of the inclined groove 57 to resist the urging force of the urging member SP. Then, the driven-side rotator 5 is slid from the locked position to the unlocked position to switch from the engaged state to the released state.

  Here, the actuator 62 for rotating the locking member 61 will be described. As shown in FIG. 6, the actuator 62 is an electromagnetic actuator in which a coil 64 a is accommodated in the first case 64 and is driven using the action of a magnetic field generated by energizing the coil 64 a.

  The first case 64 has a bottomed cylindrical shape, and a fixed core 64b is provided at the bottom thereof. The coil 64a is disposed inside the first case 64 so as to surround the fixed core 64b. That is, in the actuator 62, an electromagnet is configured by the fixed core 64b and the coil 64a. A movable core 64c is movably accommodated inside the coil 64a at a position facing the fixed core 64b. Each of the fixed core 64b and the movable core 64c is an iron core.

  A cylindrical second case 65 is attached to the distal end side (the upper end side in FIG. 6) of the first case 64. In the second case 65, a permanent magnet 65a is disposed at an end portion on the first case 64 side so as to surround the periphery of the movable core 64c. As described above, the movable core 64c is housed in the first case 64 so that the base end (the lower end in FIG. 6) faces the fixed core 64b, while the distal end (the upper side in FIG. 6). End of the second case 65 protrudes outward from the second case 65.

  A ring member 65b is attached to a portion of the movable core 64c accommodated in the second case 65. And in the 2nd case 65, the coil spring 65c is accommodated in the state compressed between this 2nd case 65 and the ring member 65b. The coil spring 65c biases the movable core 64c in a direction in which the movable core 64c protrudes from the second case 65. And the front end side which protruded from the 2nd case 65 in the movable core 64c is connected with the latching member 61 via the fixing pin 64d.

  The locking member 61 has a base end rotatably connected to the movable core 64 c and is rotatably supported by the rotation shaft 63. Therefore, the locking member 61 rotates around the rotation shaft 63 with the movement of the movable core 64c. Therefore, as shown by the solid line in FIG. 6, the degree to which the movable core 64c protrudes from the second case 65 by the urging force of the coil spring 65c is increased, so that the pin 69 of the locking member 61 is driven to the driven side rotating body 5. Can be inserted into the groove 56.

  When the coil 64a is energized in this state, the fixed core 64b and the movable core 64c are magnetized by the magnetic field generated by this energization, and the movable core 64c is pulled toward the fixed core 64b against the biasing force of the coil spring 65c. . At this time, the magnitude of the magnetic field generated in the coil 64a coincides with the direction of the magnetic field of the permanent magnet 65a.

  When the retracted movable core 64c moves in a direction approaching the fixed core 64b (downward direction in FIG. 6), the locking member 61 rotates counterclockwise in FIG. 6, and the pin 69 of the locking member 61 is moved. It is pulled out from the groove 56. That is, the actuator 62 pulls out the locking member 61 from the groove 56 by attracting the movable core 64c using the magnetic force generated by energizing the coil 64a.

  When the attracted movable core 64c moves to a position where it contacts the fixed core 64b (a position indicated by a virtual line in FIG. 6), even if energization is stopped thereafter, the movable core 64c is moved by the magnetic force of the permanent magnet 65a. The state of being in contact with the fixed core 64b is maintained.

  On the other hand, when the coil 64a is energized in the direction opposite to that when the movable core 64c is in the contact position indicated by the phantom line in FIG. 6, the direction of the magnetic field of the permanent magnet 65a is determined. A reverse magnetic field is generated. Thereby, the attractive force of the permanent magnet 65a is weakened, the movable core 64c is separated from the fixed core 64b by the biasing force of the coil spring 65c, and can be moved to the protruding position shown by the solid line in FIG. When the movable core 64 c moves from the contact position to the protruding position, the locking member 61 rotates in the clockwise direction in FIG. 6 and the pin 69 of the locking member 61 is inserted into the groove 56.

  When the movable core 64c is at a protruding position separated from the fixed core 64b, the biasing force by the coil spring 65c is larger than the attractive force by the permanent magnet 65a. Therefore, if the movable core 64c is separated from the fixed core 64b by energizing the coil 64a, the movable core 64c is held at the protruding position even if the energization is stopped thereafter.

  That is, the actuator 62 according to the present embodiment switches the connection state of the clutch device 1 by flowing the direct current in different directions and moving the movable core 64c, while maintaining the connected state or the released state. Sometimes it is a self-holding solenoid that does not require energization.

(Pin insertion restriction mechanism)
Next, a plurality of embodiments of a pin insertion restriction mechanism that is a feature of this embodiment will be described.

<First Embodiment>
First, the first embodiment will be described.

-Configuration of pin insertion restriction mechanism-
7 and 8 are diagrams for explaining the operation of the pin insertion limiting mechanism 9 in the present embodiment. FIG. 7 is a side view showing the pin insertion limiting mechanism 9 and the driven side rotating body 5 when the clutch device 1 is in an engaged state (a state corresponding to FIG. 3). FIG. 8 is a side view showing the pin insertion limiting mechanism 9 and the driven-side rotator 5 in the released state of the clutch device 1 (a state corresponding to FIG. 4). Moreover, in these figures, about the pin insertion restriction | limiting mechanism 9, the cross section along the VII-VII line in FIG. 6 is shown.

  As shown in FIG. 6, the pin insertion limiting mechanism 9 is upstream of the locking member 61 in the rotational direction of the driven-side rotating body 5 (in FIG. 6, clockwise with respect to the locking member 61. Side). That is, the pin insertion limiting mechanism 9 and the locking member 61 are disposed so as to face each other in the circumferential direction on the outer peripheral side of the driven-side rotating body 5.

  The function of the pin insertion limiting mechanism 9 is that when the locking member 61 rotates toward the groove 56 of the driven side rotating body 5 (the pin 69 is inclined by the operation of the actuator 62). When moving toward the groove 57), the rotation is prevented and the insertion of the pin 69 into the inclined groove 57 can be restricted. Further, the pin insertion limiting mechanism 9 changes state between a state where the insertion of the pin 69 into the inclined groove 57 of the driven side rotating body 5 is limited and a state where this insertion is allowed. This will be specifically described below.

  As shown in FIGS. 7 and 8, a rotation transmitting portion 59 is provided between the large diameter portion 51 and the linear groove 58 in the driven side rotating body 5. The rotation transmitting portion 59 is a portion that transmits the rotational force of the driven-side rotating body 5 to the pin insertion limiting mechanism 9 and has a smaller diameter than the outer diameter of the large diameter portion 51 and the linear groove 58. An outer peripheral surface 59a having a larger diameter than the outer diameter of the bottom surface 58b is provided. The outer peripheral surface 59a of the rotation transmitting portion 59 has a circular shape (perfect circle) centered on the axis of the driven side rotating body 5 when viewed from the axial center direction of the driven side rotating body 5. .

  Further, as shown in FIG. 6, the locking member 61 is provided with a protruding portion 66 that protrudes toward the pin insertion limiting mechanism 9 by a predetermined dimension. As will be described later, when the protrusion 66 abuts against the pin insertion restriction mechanism 9 (when the pin insertion restriction mechanism 9 is in a rotational position where it abuts against the protrusion 66), the locking member 61 rotates. The insertion of the pin 69 into the inclined groove 57 is restricted (see the state shown in FIG. 9). On the other hand, when the protrusion 66 does not contact the pin insertion restriction mechanism 9 (when the pin insertion restriction mechanism 9 is in a rotational position where it does not contact the protrusion 66), the rotation of the locking member 61 is not restricted. As a result, insertion of the pin 69 into the inclined groove 57 is allowed (see the state shown in FIG. 10). A configuration for restricting and permitting the rotation of the locking member 61 by the pin insertion limiting mechanism 9 will be described later.

  The pin insertion restriction mechanism 9 includes a support pin 91 and a rotating body 92 that is rotatably supported by the support pin 91.

  The support pin 91 is a columnar member extending along the extending direction of the axis of the driven-side rotating body 5 (the left-right direction in FIGS. 7 and 8). Further, the base end portion (right end portion in FIG. 7) of the support pin 91 is inserted into an insertion hole 93 provided in the clutch housing 2 or the like, for example. A coil spring 94 is accommodated in a compressed state between the base end portion of the support pin 91 and the bottom of the insertion hole 93, and the coil spring 94 biases the support pin 91 in the left direction in FIG. The urging force to go is given. Further, the tip end portion (the left end portion in FIG. 7) of the support pin 91 is in contact with the end face 51 b of the large diameter portion 51 of the driven side rotating body 5. That is, the support pin 91 receives the urging force from the coil spring 94, so that the tip portion is pressed against the end surface 51 b of the large-diameter portion 51 of the driven-side rotating body 5. For this reason, when the driven-side rotator 5 slides from the locked position (the state shown in FIG. 7) to the unlocked position (the state shown in FIG. 8), the support pin 91 is driven. In response to the slide movement, the coil spring 94 is inserted into the insertion hole 93 while being compressed and deformed (moves to the right in FIG. 8).

  In order to prevent wear of the tip portion of the support pin 91, it is preferable that a thrust bearing is interposed between the end surface 51 b of the large diameter portion 51 and the tip portion of the support pin 91.

  The rotating body 92 is rotatably supported by the support pin 91 as described above. The rotating body 92 includes a rotation receiving portion 92a having a small diameter, and an eccentric cam 92b (regulating member referred to in the present invention) having a larger diameter than the rotation receiving portion 92a and integrally formed with the rotation receiving portion 92a. It has.

  The rotationally transmitted portion 92 a has a cylindrical shape, and its axis coincides with the axis of the support pin 91. In other words, the rotationally transmitted portion 92a is rotatable about the axis of the support pin 91 as a rotation center. In addition, the cross-sectional shape in the direction orthogonal to the axis of the rotationally transmitted portion 92a is a perfect circle. An outer peripheral surface 92c of the rotation transmitted portion 92a is in contact with an outer peripheral surface 59a of the rotation transmitting portion 59 of the driven side rotating body 5. For this reason, the rotational force of the driven-side rotator 5 is transmitted from the rotation transmitting portion 59 to the rotation-transmitted portion 92a, so that the rotator 92 rotates around the support pin 91 by the rotation of the driven-side rotator 5. It is designed to rotate in sync with.

  The outer diameter dimension of the rotation transmitting portion 59 is an integral multiple of the outer diameter dimension of the rotation transmitted portion 92a. Each time the rotation transmitting portion 59 rotates, the rotation transmitted portion 92a rotates by an integral multiple. It is like that.

  In order to smoothly rotate the rotating body 92, it is preferable that a needle bearing is interposed between the rotating body 92 and the support pin 91.

  On the other hand, the eccentric cam 92b has a cylindrical shape, and its axis is eccentric by a predetermined length with respect to the axis of the support pin 91 and the axis of the rotationally transmitted portion 92a. Further, the eccentric cam 92b has a protrusion 66 (shown in phantom lines in FIG. 7) of the locking member 61 when the driven-side rotator 5 is in the locked position (position shown in FIG. 7). It is in the position facing. Further, the eccentric cam 92b is provided with a protruding portion 66 (shown in phantom lines in FIG. 8) of the locking member 61 when the driven-side rotator 5 slides to the unlock position (position shown in FIG. 8). The position moves to the position not facing (the position retracted from the position facing the protrusion 66; the position on the right side in FIG. 8 and the position on the back side of the sheet in FIG. 6).

  As described above, the shaft center of the eccentric cam 92b is eccentric by a predetermined length with respect to the shaft center of the support pin 91 and the shaft center of the rotationally transmitted portion 92a. That is, as the shape of the outer peripheral surface of the eccentric cam 92b, the distance from the axis of the support pin 91 in each part of the outer peripheral surface is unequal. For this reason, when the eccentric cam 92b rotates as the rotational force of the driven-side rotating body 5 is transmitted to the rotating body 92, a region where the distance from the axis of the support pin 91 is long (generally an eccentric portion or nose). A region called a portion) approaching the locking member 61 (more specifically, the protrusion 66 of the locking member 61) and a region where the distance from the axis of the support pin 91 is short (generally called a base circle portion). The state in which the region is approaching the locking member 61 is periodically visited. Here, among the outer peripheral surfaces of the eccentric cam 92b, the outer peripheral surface whose distance from the shaft center of the support pin 91 is longer than a predetermined length is referred to as “interference outer surface (the outer surface that interferes with the protrusion 66 of the locking member 61 as described later). The outer peripheral surface whose distance from the axis of the support pin 91 is shorter than a predetermined length is referred to as “a non-interfering outer surface (an outer surface that does not interfere with the protruding portion 66 of the locking member 61 as will be described later). ) ”).

  When the outer diameter dimension of the rotation transmitting part 59 is twice the outer diameter dimension of the rotation transmitted part 92a, the interference outer surface becomes the locking member every time the driven side rotating body 5 makes one rotation. A state in which it approaches 61 and a state in which the non-interfering outer surface approaches the locking member 61 are periodically visited twice. Further, when the outer diameter of the rotation transmitting portion 59 is three times the outer diameter of the rotationally transmitted portion 92a, the interference outer surface becomes the locking member every time the driven-side rotating body 5 makes one rotation. The state in which it approaches 61 and the state in which the non-interfering outer surface approaches the locking member 61 come periodically three times.

  As shown in FIG. 9, when the interference outer surface is close to the locking member 61, even when the locking member 61 is rotated toward the inclined groove 57 by the operation of the actuator 62, The protrusion 66 of the locking member 61 and the eccentric cam 92b (interference outer surface of the eccentric cam 92b) interfere with each other, and the rotation of the locking member 61 is restricted. That is, the insertion of the pin 69 into the inclined groove 57 of the driven side rotating body 5 is limited.

  On the other hand, as shown in FIG. 10, when the non-interference outer surface is close to the locking member 61, if the locking member 61 is rotated toward the inclined groove 56 by the operation of the actuator 62, The protrusion 66 of the locking member 61 does not interfere with the eccentric cam 92b (the non-interfering outer surface of the eccentric cam 92b), and the rotation of the locking member 61 is not limited. That is, the insertion of the pin 69 into the inclined groove 57 of the driven side rotating body 5 is not limited (allowed).

  The outer diameter dimension of the eccentric cam 92b and the eccentric length with respect to the axis of the support pin 91 are appropriately set by experiments or the like so that the above-described interference state and non-interference state can be realized.

  Next, the range in which the rotation of the locking member 61 is restricted by the pin insertion restriction mechanism 9 will be specifically described.

  As described above with reference to FIGS. 16 and 17, in the case of the configuration without the pin insertion restriction mechanism 9, depending on the timing at which the locking member a starts to rotate, the locking member (pin ) During the insertion operation of a (in a state where the insertion operation is not completed), the side surface b1 of the inclined groove b may come into contact with the locking member a. That is, there is a possibility that the side surface b1 of the inclined groove b contacts the locking member a in a state where the amount of the locking member a inserted into the inclined groove b is small (the insertion depth is shallow). In this way, when the side surface b1 of the inclined groove b contacts the locking member a, the contact load from the side surface b1 of the inclined groove b is only when the contact is started. Will receive. For this reason, the contact load which acts on the front-end | tip part of this latching member a will become extremely large. If such a large contact load is frequently applied, a part (tip portion) of the locking member a may be worn away, which may adversely affect the releasing operation of the clutch device, There is a possibility of adversely affecting the life extension. Moreover, a part of the side surface of the inclined groove b may be worn by the contact load.

  In order to avoid the occurrence of this situation, in the present embodiment, a predetermined region in the inclined groove 57 of the driven-side rotating body 5 (as described above, with the insertion amount of the engaging member being small, the engaging member is provided with the inclined groove). The insertion of the pin 69 into the area where the side surfaces come into contact; hereinafter referred to as “pin insertion restriction request area”) is restricted by the pin insertion restriction mechanism 9.

  This pin insertion restriction request region is a region where the driven-side rotating body 5 is shaded in FIGS. 9 and 10 (the portion of the inclined groove 57 in the shaded region). Specifically, FIG. 11 (development of the inclined groove forming area of the driven-side rotating body 5 and the pin insertion restriction request area, the pin insertion request area, the rotational position of the eccentric cam 92b, and the sliding position of the rotating body 92 This will be described with reference to FIG.

  In the rotational position of the eccentric cam 92b in FIG. 11, the “interference rotational position” is a rotational position where the interference outer surface of the eccentric cam 92b is close to the locking member 61 (the interference outer surface of the eccentric cam 92b is the locking member 61). The “non-interfering rotational position” is a rotational position where the non-interfering outer surface of the eccentric cam 92b is close to the locking member 61 (the eccentric cam 92b is protruding from the locking member 61). (Rotational position that does not interfere with the portion 66).

  As shown in FIG. 11, a region extending from the formation range t3 of the pin insertion side surface 57aI to the formation range t2 of the inclined side surface 57aII is the pin insertion restriction request region (region where insertion of the pin 69 should be prevented). Yes. More specifically, from a position displaced by 5 ° to the downstream side (left side in FIG. 11) in the rotational direction of the driven-side rotating body 5 with respect to the boundary part β of the formation ranges t3 and t2, the boundary part β On the other hand, a range up to a position displaced by 40 ° on the upstream side (right side in FIG. 11) in the rotation direction of the driven-side rotating body 5 is a pin insertion restriction request region.

  The pin 69 (more specifically, the tip position of the pin 69 (the upstream position in the rotational direction of the driven rotating body 5)) faces this pin insertion restriction request region (for example, the pin 69 in FIG. 11). When the pin 69 moves toward the inclined groove 57 (in the position indicated by the phantom line Y), the pin 69 is inclined with a small insertion amount (the insertion depth is shallow). The inclined side surface 57aII of the groove 57 moves toward the pin 69, and the inclined side surface 57aII may come into contact with the pin 69 in a state where the amount of insertion is small. For this reason, this pin insertion restriction request area is defined as an area where insertion of the pin 69 should be restricted. In addition, each said value is not limited to these, It sets suitably.

  Further, a range other than the pin insertion restriction request region in the formation range t3 of the pin insertion side surface 57aI is a pin insertion request region.

  When the pin 69 moves toward the inclined groove 57 in a state where the pin 69 faces the pin insertion request region (for example, in a state where the pin 69 is in a position indicated by a solid line in FIG. 11), the inclined groove 57 In a state where the insertion of the pin 69 into the pin is completed (the insertion depth of the pin 69 is deep), the inclined side surface 57aII of the inclined groove 57 moves toward the pin 69. That is, it is possible to avoid the inclined side surface 57aII coming into contact with the pin 69 in a state where the insertion amount of the pin 69 is small. For this reason, this pin insertion request area is defined as an area where insertion of the pin 69 should be allowed.

  Further, in the region that is neither the pin insertion restriction request region nor the pin insertion request region (the pin insertion impossibility region in FIG. 11), even if the pin 69 moves toward this region, the pin 69 is driven side rotating body. 5 (for example, the circular arc surface 57aIII) and the insertion into the inclined groove 57 is prevented (see the position of the pin 69 indicated by the phantom line X in FIG. 11).

  In order to realize the insertion of the pin 69 only from the pin insertion request region, the eccentric cam 92b is configured such that the interference outer surface is the locking member 61 in a situation where the pin insertion restriction request region faces the pin 69. It will be in a state of approaching. As a result, even when the locking member 61 rotates toward the inclined groove 57, the protrusion 66 of the locking member 61 and the eccentric cam 92b (interference outer surface of the eccentric cam 92b) interfere with each other, The locking member 61 is prevented from rotating (in the case of the present invention, “when the locking member faces the insertion restriction request area, the interference from the rotation axis is long in the regulating member). This corresponds to “the insertion of the locking member into the inclined groove is restricted when the outer surface interferes with the locking member”).

  Specifically, in FIG. 9 and FIG. 10, the outer peripheral surface in the hatched region of the rotating body 92 is the interference outer surface (the outer surface that interferes with the protrusion 66 of the locking member 61), and this interference outer surface is During the period of facing the locking member 61, the interference outer surface interferes with the protrusion 66, thereby preventing the locking member 61 from rotating (see the state shown in FIG. 9). That is, the range where the interference outer surface interferes with the protruding portion 66 of the locking member 61 corresponds to the range where the pin 69 faces the pin insertion restriction request region. In other words, the period in which the pin 69 faces the pin insertion restriction request region and the period in which the interference outer surface of the eccentric cam 92b interferes with the protrusion 66 of the locking member 61 are synchronized ( (Refer to the point that the pin insertion restriction request region in FIG. 11 coincides with the interference rotation position at the rotation position of the eccentric cam 92b).

  As described above, the outer diameter size of the rotation transmitting portion 59 is an integral multiple of the outer diameter size of the rotation receiving portion 92a, and each time the rotation transmitting portion 59 makes one rotation, the rotation receiving portion 92a It is designed to rotate by an integral multiple. For this reason, when the pin 69 faces the pin insertion restriction request region, the interference outer surface of the eccentric cam 92b always interferes with the protrusion 66 of the locking member 61. For this reason, it is possible to synchronize the period in which the pin 69 faces the pin insertion restriction request region and the period in which the interference outer surface of the eccentric cam 92 b interferes with the protrusion 66 of the locking member 61.

  On the other hand, the eccentric cam 92 b is in a state where the non-interfering outer surface approaches the locking member 61 in a situation where the pin insertion request region faces the pin 69. The non-interference outer surface has a shorter eccentric length with respect to the axis of the support pin 91 than the interference outer surface. For this reason, this non-interfering outer surface does not interfere with the protrusion 66 of the locking member 61, and if the locking member 61 rotates toward the inclined groove 57, the locking member 61 rotates. (In the present invention, “when the locking member is in a region other than the forming range of the inclined side surface in the inclined groove and faces the predetermined insertion requirement region, it is rotated in the regulating member. This is equivalent to the fact that the non-interfering outer surface with a short distance from the shaft center faces the locking member, so that the locking member does not interfere and insertion of the locking member into the inclined groove is permitted.

  Specifically, in FIG. 9 and FIG. 10, the outer peripheral surface in the region where the rotating body 92 is not shaded is the non-interfering outer surface (the outer surface that does not interfere with the protruding portion 66 of the locking member 61). During the period in which the non-interfering outer surface faces the locking member 61, the non-interfering outer surface does not interfere with the protrusion 66, and the locking member 61 is allowed to rotate (shown in FIG. 10). See state). That is, the range where the non-interfering outer surface faces the protruding portion 66 of the locking member 61 corresponds to the range where the pin 69 faces the pin insertion request region. In other words, the period in which the pin 69 faces the pin insertion request region and the period in which the non-interfering outer surface of the eccentric cam 92b faces the protrusion 66 of the locking member 61 are synchronized. (Refer to the point that the pin insertion request area in FIG. 11 and the non-interference rotational position at the rotational position of the eccentric cam 92b coincide).

  As described above, the outer diameter size of the rotation transmitting portion 59 is an integral multiple of the outer diameter size of the rotation transmitted portion 92a. For this reason, the non-interfering outer surface of the eccentric cam 92 b always faces the protruding portion 66 of the locking member 61 in a state where the pin 69 faces the pin insertion request region. For this reason, it is possible to synchronize the period in which the pin 69 faces the pin insertion request region and the period in which the non-interfering outer surface of the eccentric cam 92 b faces the protrusion 66 of the locking member 61.

  Further, as described above, when the driven-side rotating body 5 slides from the locked position (state shown in FIG. 7) to the unlocked position (state shown in FIG. 8), the support pin 91 causes the coil spring 94 to move in the compression direction. It is inserted into the insertion hole 93 while being deformed. Along with this, the rotating body 92 also moves, and the eccentric cam 92b is retracted to a position where it does not interfere with the protruding portion 66 of the locking member 61. That is, when the pin 69 is inserted into the groove 56 and the driven-side rotator 5 slides toward the unlock position, the interference outer surface is brought into contact with the protrusion 66 of the locking member 61 by the rotation of the rotator 92. Even if they are close to each other, the position of the interference outer surface is offset in the direction along the axis with respect to the protrusion 66, so that the eccentric cam 92b does not interfere with the protrusion 66 (the eccentric cam in FIG. 8). (Refer to the relationship between the position of 92b and the position of the protrusion 66 indicated by the phantom line). That is, even if the eccentric cam 92b rotates after the pin 69 is once inserted into the groove 56 and the driven-side rotator 5 slides toward the unlock position, the eccentric cam 92b is There is no interference with the protrusion 66. In the slide position of the rotating body 92 in FIG. 11, the “interference-possible position” is a position where the driven-side rotating body 5 is in the locked position and the eccentric cam 92b faces the protrusion 66 of the locking member 61 (interference outer surface). Is a position that can interfere with the protrusion 66; the position shown in FIG. 7, and the “retracted position” is a position where the driven-side rotating body 5 is moving from the lock position toward the unlock position or the unlock position. In this case, the eccentric cam 92b does not face the protruding portion 66 of the locking member 61 (the offset position) (the position where the interference outer surface cannot interfere with the protruding portion 66; the position shown in FIG. 8).

-Operation of the clutch device-
Next, the operation of the clutch device 1 configured as described above will be described.

  When the movable core 64c of the actuator 62 is in the contact position, the pin 69 of the locking member 61 is retracted from the groove 56, as indicated by a virtual line in FIG. At this time, as shown in FIG. 3, since the driven side rotating body 5 is held in the locked position by the biasing force of the biasing member SP, the spherical body 31 is positioned in the connecting groove portion 55, and the clutch device 1 is In the engaged state. That is, the clutch device 1 transmits the rotation of the driving side rotating body 4 to the clutch output shaft 11 via the driven side rotating body 5. Thereby, the water pump 8 is operating. Further, in this case, as shown in FIG. 7, the support pin 91 of the pin insertion limiting mechanism 9 is in the advanced position under the urging force of the coil spring 94, and the eccentric cam 92 b is in the protruding portion 66 of the locking member 61. And it exists in the position which faced the inclination groove | channel 57, respectively. The rotating body 92 is rotated by receiving the rotational force of the driven side rotating body 5.

  In the operating state of the water pump 8, when the coil 64a of the actuator 62 is energized so as to generate a magnetic field opposite to the direction of the magnetic field of the permanent magnet 65a, the movable core 64c is brought into contact with the urging force of the coil spring 65c. To the protruding position indicated by the solid line in FIG. Then, as the locking member 61 rotates in the clockwise direction in FIG. 6, the pin 69 of the locking member 61 moves toward the inclined groove 57 of the driven side rotating body 5.

As described above, when the pin 69 of the locking member 61 moves toward the inclined groove 57 of the driven side rotating body 5, there are the following three patterns as the process of inserting the pin 69 into the inclined groove 57.
(1) When the locking member 61 rotates with the pin 69 facing the pin insertion restriction request area, and the pin 69 moves toward the pin insertion restriction request area,
(2) When the locking member 61 is rotated in a state where the pin 69 faces the pin insertion-impossible region, and the pin 69 moves toward the pin insertion-impossible region,
(3) When the locking member 61 rotates at a position where the pin 69 faces the pin insertion request area, and the pin 69 moves toward the pin insertion request area,
Hereinafter, each case will be described.

(1) When the pin moves toward the pin insertion restriction request region As an example of this case, the pin 69 moves toward the inclined groove 57 in the state indicated by the phantom line Y in FIG. .

  In this case, as described above, the sliding position of the rotating body 92 is an interference capable position (a position where the eccentric cam 92b faces the protruding portion 66 of the locking member 61), and the rotation of the eccentric cam 92b. The position is an interference rotation position where the interference outer surface faces the locking member 61. For this reason, the protrusion 66 of the locking member 61 and the eccentric cam 92b interfere with each other, and the rotation of the locking member 61 is limited (see FIG. 9). Therefore, the insertion of the pin 69 from this pin insertion restriction request area is prevented.

  Thereafter, as the rotation of the driven-side rotator 5 proceeds, the rotator 92 also rotates, and the rotational position of the eccentric cam 92b is a non-interfering rotational position where the non-interfering outer surface faces the locking member 61. At this time, since the pin 69 faces the pin insertion-impossible region of the inclined groove 57 (see the position of the pin 69 indicated by the phantom line X in FIG. 11), the insertion into the inclined groove 57 is still prevented.

  When the rotating body 92 further rotates as the driven-side rotating body 5 further rotates, when the pin 69 faces the pin insertion request region of the inclined groove 57, the rotational position of the eccentric cam 92b is the non-interfering outer surface. Becomes a non-interference rotation position that approaches the locking member 61, and the protrusion 66 of the locking member 61 and the eccentric cam 92b do not interfere with each other, and the locking member 61 is allowed to rotate (see FIG. 10). . Accordingly, the pin 69 is inserted from the pin insertion request region and guided toward the bottom surface 57b of the inclined groove 57.

(2) When the pin moves toward the pin insertion-impossible region An example of this case is a case where the pin 69 moves toward the inclined groove 57 in the state indicated by the virtual line X in FIG.

  In this case, even if the rotational position of the eccentric cam 92b of the pin insertion limiting mechanism 9 becomes the non-interference rotational position, the pin 69 faces the pin insertion impossible region of the inclined groove 57, so that the inclined groove 57 Insertion into is prevented.

  Further, if the rotational position of the eccentric cam 92b of the pin insertion limiting mechanism 9 is the interference rotational position, the protruding portion 66 of the locking member 61 and the eccentric cam 92b interfere with each other as in the case described above. The rotation of the locking member 61 is limited. For this reason, the insertion of the pin 69 into the inclined groove 57 is prevented.

  When the rotation of the driven-side rotator 5 advances and the pin 69 faces the pin insertion request area of the inclined groove 57, the rotational position of the eccentric cam 92b becomes the non-interference rotational position, and the locking member 61 The protrusion 66 and the eccentric cam 92b do not interfere with each other, and the locking member 61 is allowed to rotate. Accordingly, the pin 69 is inserted from the pin insertion request region and guided toward the bottom surface 57b of the inclined groove 57.

(3) When the pin moves toward the pin insertion request region As an example of this case, the pin 69 moves toward the inclined groove 57 in the state indicated by the solid line in FIG.

  In this case, the pin 69 faces the pin insertion required region of the inclined groove 57. The rotational position of the eccentric cam 92b of the pin insertion limiting mechanism 9 is a non-interference rotational position, and interference between the protruding portion 66 of the locking member 61 and the eccentric cam 92b is eliminated. In other words, the locking member 61 is allowed to rotate. For this reason, the pin 69 is inserted into the inclined groove 57 from the pin insertion required region and guided toward the bottom surface 57b of the inclined groove 57.

  When the pin 69 is inserted from the pin insertion request region of the inclined groove 57 through the above process, the pin 69 is inserted in the inclined groove 57 (the insertion depth of the pin 69 is deep). The driven-side rotating body 5 rotates together with the driving-side rotating body 4 while reaching the forming range of the inclined side face 57aII from the forming range of the pin insertion side face 57aI and in contact with the inclined side face 57aII. Then, while the pin 69 relatively moves in the inclined groove 57, the driven-side rotator 5 moves from the locked position toward the unlocked position. That is, the state changes from the state shown in FIGS. 3 and 7 to the state shown in FIGS. 4 and 8. Thereafter, when the rotation of the driven-side rotating body 5 proceeds, the pin 69 is inserted into the linear groove 58 from the terminal end portion 57d of the inclined groove 57 through the start end portion 58c of the linear groove 58. As a result, the driven-side rotator 5 reaches the unlock position. When the driven-side rotator 5 reaches the unlocked position, the sphere 31 is positioned in the connection release groove 54, and the rotation of the drive-side rotator 4 is not transmitted to the driven-side rotator 5, and the clutch device 1 Is released.

  Immediately after the connection between the driven-side rotating body 5 and the driving-side rotating body 4 is released, the driven-side rotating body 5 is in a state where the pin 69 is inserted into the linear groove 58, as shown in FIG. While being affected by the frictional force generated between the pins 69, the rotation is continued by the inertial force. In this state, when the pin 69 is inserted into the linear groove 58, the pin 69 is engaged with the step existing at the boundary between the inclined groove 57 and the linear groove 58, that is, the side surface 58 a of the linear groove 58. Therefore, the pin 69 is not displaced into the inclined groove 57 unless the pin 69 is displaced so as to be pulled out from the linear groove 58 and overcomes this step. Thus, in a state where the pin 69 of the locking member 61 is inserted into the linear groove 58 of the driven-side rotator 5, the driven-side rotator 5 rotates, and the rotation speed gradually decreases. When this state is continued, the water pump 8 is stopped.

  On the other hand, when the clutch device 1 is switched from the released state to the engaged state, the coil 64a of the actuator 62 is energized so as to generate a magnetic field having the same direction as the direction of the magnetic field of the permanent magnet 65a. Then, the movable core 64c is attracted so as to approach the fixed core 64b by the magnetic force generated by energization, and moves from the protruding position indicated by the solid line to the contact position indicated by the phantom line in FIG. As a result, the locking member 61 rotates counterclockwise in FIG. 6 and the pin 69 of the locking member 61 is completely pulled out from the groove 56.

  Then, the driven side rotating body 5 released from the locking by the locking member 61 is moved to the lock position by the biasing force of the biasing member SP, and the driven side rotating body 5 and the driving side rotating body 4 are connected. Then, the clutch device 1 is switched to the engaged state. As the driven-side rotator 5 moves to the lock position, the eccentric cam 92b returns to the position facing the protrusion 66 and the inclined groove 57 of the locking member 61, respectively.

  Since the engaged state and the released state of the clutch device 1 are thus switched, as described above, the period during which the clutch device 1 is engaged and the period during which the clutch device 1 is released within a predetermined period. By adjusting the ratio, the rotational speed of the water pump 8 can be arbitrarily adjusted.

  As described above, in the present embodiment, when the pin 69 faces the pin insertion restriction request region of the inclined groove 57, the interference outer surface of the eccentric cam 92 b of the pin insertion restriction mechanism 9 is the locking member 61. By interfering with the protrusion 66, insertion of the pin 69 into the inclined groove 57 is restricted. On the other hand, when the pin 69 faces the pin insertion request region of the inclined groove 57, the non-interfering outer surface of the eccentric cam 92b of the pin insertion restriction mechanism 9 faces the protrusion 66 of the locking member 61. Insertion of the pin 69 into the inclined groove 57 is allowed without interfering with the locking member 61.

  For this reason, when the pin 69 starts to move forward toward the inclined groove 57, the movement of the inclined side surface 57aII of the inclined groove 57 toward the portion where the pin 69 is inserted has already started. There is no invitation. That is, it is avoided that the inclined side surface 57aII of the inclined groove 57 contacts the pin 69 in a state where the insertion amount of the pin 69 into the inclined groove 57 is small (the insertion depth is shallow). In other words, when the pin 69 starts moving forward toward the inclined groove 57, the movement of the inclined side surface 57aII of the inclined groove 57 toward the portion where the pin 69 is inserted is not yet started. be able to. That is, the inclined side surface 57aII of the inclined groove 57 can be brought into contact with the pin 69 in a state where the insertion amount of the pin 69 with respect to the inclined groove 57 is large (the insertion depth is deep).

  As described above, since the region where the pin 69 can be inserted into the inclined groove 57 is defined, the contact load acting on the tip portion of the pin 69 can be reduced, and wear of the tip portion of the pin 69 is suppressed. can do. As a result, the operation for bringing the clutch device 1 into the released state is not adversely affected. In addition, the life of the pin 69 can be extended. Further, by reducing the contact load, wear of the inclined side surface 57aII of the inclined groove 57 can be suppressed. This also does not adversely affect the operation for bringing the clutch device 1 into the released state. In addition, the life of the driven-side rotating body 5 can be extended.

Second Embodiment
Next, a second embodiment of the pin insertion restriction mechanism 9 will be described. In the present embodiment, the moving direction of the pin insertion limiting mechanism 9 when the driven-side rotator 5 slides from the locked position toward the unlocked position (the eccentric cam 92b retracts from the protrusion 66 of the locking member 61). Direction) is different from that of the first embodiment. Here, only differences from the first embodiment will be described.

  12 and 13 are diagrams for explaining the operation of the pin insertion limiting mechanism 9 in the present embodiment. FIG. 12 is a side view showing the pin insertion limiting mechanism 9 and the driven-side rotator 5 when the clutch device 1 is engaged (a state corresponding to FIG. 3). FIG. 13 is a side view showing the pin insertion limiting mechanism 9 and the driven-side rotator 5 in the released state of the clutch device 1 (a state corresponding to FIG. 4).

  As shown in FIGS. 12 and 13, in the present embodiment, the rotation transmitting portion 59 provided between the large-diameter portion 51 and the linear groove 58 in the driven-side rotator 5 is an outer peripheral surface 59b. Has a circular arc shape in cross section. Specifically, it is a circular arc surface that is recessed so that the outer diameter dimension gradually decreases from the large diameter portion 51 toward the linear groove 58.

  The pin insertion limiting mechanism 9 in this embodiment also includes a support pin 91 and a rotating body 92 that is rotatably supported by the support pin 91.

  The support pin 91 is a columnar member that extends along the axis of the driven rotating body 5 (the left-right direction in FIGS. 12 and 13), as in the first embodiment. A coil spring 95 is attached to the base end portion (right end portion in FIG. 12) of the support pin 91. The coil spring 95 is disposed in a compressed state between a proximal end portion of the support pin 91 and a spring mounting seat 96 disposed above the proximal end portion of the support pin 91. As a result, the support pin 91 receives a downward biasing force from the coil spring 95. The spring mounting seat 96 is provided on the clutch housing 2 or the like.

  Similar to the first embodiment, the rotating body 92 includes a rotation transmitted portion 92a and an eccentric cam 92b.

  The outer peripheral surface 92d of the rotationally transmitted portion 92a is a circular arc surface having a convex cross section along the axis. An outer peripheral surface 92d of the rotation transmitted portion 92a is in contact with an outer peripheral surface 59b of the rotation transmitting portion 59 of the driven side rotating body 5. For this reason, the rotational force of the driven-side rotator 5 is transmitted from the rotation transmitter 59 to the rotation receiver 92 a, and the rotator 92 rotates around the support pin 91.

  When the driven-side rotator 5 slides from the locked position (state shown in FIG. 12) to the unlocked position (state shown in FIG. 13), the rotator 92 pushes from the outer peripheral surface 59b of the rotation transmitting portion 59. Under pressure. As described above, the outer peripheral surface 59 b of the rotation transmitting portion 59 is a circular arc surface that is recessed so that the outer diameter dimension gradually decreases from the large diameter portion 51 toward the linear groove 58. For this reason, the rotating body 92 moves in a direction away from the axis of the driven-side rotating body 5 (upward in FIG. 13) while the coil spring 95 is deformed in the compression direction by the pressing force received from the outer peripheral surface 59b. It is like that.

  The configuration of the eccentric cam 92b is the same as that of the first embodiment, and the distance from the axis of the support pin 91 in each part of the outer peripheral surface is unequal. That is, an interference outer surface having a long distance from the axis of the support pin 91 and a non-interference outer surface having a short distance from the axis of the support pin 91 are provided.

  As shown in FIG. 14, when the interference outer surface is close to the locking member 61, even if the locking member 61 is rotated toward the inclined groove 57, The protrusion 66 and the eccentric cam 92b (interference outer surface of the eccentric cam 92b) interfere with each other, and the rotation of the locking member 61 is restricted. That is, the insertion of the pin 69 into the inclined groove 57 of the driven side rotating body 5 is limited.

  On the other hand, when the non-interfering outer surface is close to the locking member 61, the locking member 61 is rotated toward the inclined groove 56, and the protrusion 66 and the eccentric cam 92 b (eccentricity) of the locking member 61 are rotated. The non-interfering outer surface of the cam 92b does not interfere, and the rotation of the locking member 61 is not limited. That is, the insertion of the pin 69 into the inclined groove 57 of the driven side rotating body 5 is not limited (allowed).

  In the present embodiment, when the driven-side rotating body 5 slides from the locked position (the state shown in FIGS. 12 and 14) to the unlocked position (the state shown in FIGS. 13 and 15), the support pin 91 moves in a direction away from the axis of the driven-side rotating body 5 while deforming the coil spring 95 in the compression direction (see the arrow shown in FIG. 15). Along with this, the rotating body 92 also moves, and the eccentric cam 92b is retracted to a position where it does not interfere with the protruding portion 66 of the locking member 61. That is, in the state where the pin 69 is inserted into the groove 56, the eccentric cam 92 b does not interfere with the protruding portion 66 of the locking member 61 even if the rotating body 92 rotates. In the state shown in FIG. 15, the position of the eccentric cam 92 b is the same as that in FIG. 14 (the state where the eccentric cam 92 b interferes with the protruding portion 66 of the locking member 61), but the rotating body 92 is moving (covered). As a result, the eccentric cam 92b does not interfere with the protruding portion 66 of the locking member 61.

  Other configurations and operations of the clutch device 1 are the same as those of the first embodiment described above.

  Also in this embodiment, the same effect as in the case of the first embodiment can be obtained. That is, when the pin 69 faces the pin insertion restriction request region of the inclined groove 57, the interference outer surface of the eccentric cam 92b of the pin insertion restriction mechanism 9 interferes with the protruding portion 66 of the locking member 61, thereby inclining. Insertion of the pin 69 into the groove 57 is restricted. On the other hand, when the pin 69 faces the pin insertion request region of the inclined groove 57, the non-interfering outer surface of the eccentric cam 92b of the pin insertion restriction mechanism 9 faces the protrusion 66 of the locking member 61. Insertion of the pin 69 into the inclined groove 57 is allowed without interfering with the locking member 61.

  For this reason, when the pin 69 starts to move forward toward the inclined groove 57, the movement of the inclined side surface 57aII of the inclined groove 57 toward the portion where the pin 69 is inserted has already started. There is no invitation. That is, it is avoided that the inclined side surface 57aII of the inclined groove 57 contacts the pin 69 in a state where the insertion amount of the pin 69 into the inclined groove 57 is small (the insertion depth is shallow). In other words, when the pin 69 starts moving forward toward the inclined groove 57, the movement of the inclined side surface 57aII of the inclined groove 57 toward the portion where the pin 69 is inserted is not yet started. be able to. That is, the inclined side surface 57aII of the inclined groove 57 can be brought into contact with the pin 69 in a state where the insertion amount of the pin 69 with respect to the inclined groove 57 is large (the insertion depth is deep).

  As described above, since the region where the pin 69 can be inserted into the inclined groove 57 is defined, the contact load acting on the tip portion of the pin 69 can be reduced, and wear of the tip portion of the pin 69 is suppressed. can do. As a result, the operation for bringing the clutch device 1 into the released state is not adversely affected. In addition, the life of the pin 69 can be extended. Further, by reducing the contact load, wear of the inclined side surface 57aII of the inclined groove 57 can be suppressed. This also does not adversely affect the operation for bringing the clutch device 1 into the released state. In addition, the life of the driven-side rotating body 5 can be extended.

-Other embodiments-
In each embodiment described above, the groove depth in the formation range t2 of the inclined side surface 57aII of the inclined groove 57 is uniform over the circumferential direction. The present invention is not limited to this, and may be configured to gradually become deeper from the start end portion 57c to the end portion 57d in the formation range t2 of the inclined side surface 57aII.

  In each of the above embodiments, the outer peripheral surface 59a of the rotation transmitting portion 59 of the driven-side rotating body 5 and the outer peripheral surface 92c of the rotation transmitting portion 92a of the rotating body 92 are both curved surfaces (arc-shaped surfaces). When these are in line contact, the rotational force of the driven-side rotator 5 is transmitted to the rotator 92. The present invention is not limited to this, and gears are formed on the outer peripheral surface of the rotation transmitting portion 59 and the outer peripheral surface of the rotation transmitted portion 92a, respectively, and the rotational force of the driven-side rotating body 5 is applied to the rotating body 92 by meshing these gears. You may make it transmit. Accordingly, the rotational force is reliably transmitted to the rotating body 92, and the driven-side rotating body 5 and the rotating body 92 are appropriately synchronized. In addition, as a configuration for synchronously rotating the driven-side rotator 5 and the rotator 92, the driven-side rotator 5 and the rotator 92 may be connected by a transmission belt.

  In each of the above embodiments, the pin insertion restriction request region of the inclined groove 57 and the interference rotation position of the eccentric cam 92b are synchronized. In other words, the period in which the pin 69 faces the pin insertion restriction request region and the period in which the interference outer surface interferes with the protrusion 66 of the locking member 61 are synchronized. The present invention is not limited to this, and the interference rotation position of the eccentric cam 92b with respect to the pin insertion restriction request region of the inclined groove 57 may be expanded upstream in the rotation direction of the driven-side rotating body 5. In other words, even after the period in which the pin 69 faces the pin insertion restriction request region has elapsed (even in the period in which the pin 69 faces the pin insertion-incapable region), the interference outer surface is the protruding portion 66 of the locking member 61. You may make it continue the state which interferes with only for a predetermined period.

  Further, in each of the embodiments described above, the depth of the linear groove 58 is constant over the entire circumference. The present invention is not limited to this, and the groove depth of the start end portion 58c in the linear groove 58 may be shallower than the groove depth of other portions.

  Further, in each of the above embodiments, the grooves 56 (inclined grooves 57 and linear grooves 58) into which the pins 69 of the locking member 61 are inserted are provided on the outer peripheral surface of the driven side rotating body 5. The present invention is not limited to this, and these grooves 56 are provided on the inner peripheral surface of the driven-side rotator 5, and the pin 69 of the locking member 61 inserted into the inner space of the driven-side rotator 5 moves to the outer peripheral side. It is good also as a structure inserted in the groove | channel 56 by doing. In this case, the pin insertion limiting mechanism 9 is also disposed on the inner peripheral side of the driven-side rotating body 5, and prevents the pin 69 of the locking member 61 from moving to the outer peripheral side.

  The number of the urging members SP can be arbitrarily changed. For example, the driven side rotating body 5 can be urged by one urging member. The urging member SP may be any member that urges the driven-side rotator 5 toward the lock position, and is not limited to the compression coil spring described above. For example, a tension spring that pulls the driven-side rotating body 5 toward the lock position may be applied as the biasing member.

  The actuator 62 is not limited to a self-holding solenoid. For example, the actuator 62 may be a solenoid in which the locking member 61 is inserted into the groove 56 only while the coil is energized. According to this configuration, since the clutch device 1 is in the released state only when the coil is energized, the clutch device 1 is in the engaged state when the coil cannot be energized. Accordingly, the water pump 8 can be driven even when the actuator 62 is malfunctioning.

  The actuator 62 is not limited to a solenoid, and may be an actuator other than a solenoid, such as a hydraulic actuator.

  The configuration of the clutch device 1 is not limited to the ball lock type. For example, a crimp type clutch device may be used.

  In each of the above embodiments, the case where the present invention is applied to the clutch device 1 that switches the transmission state of power from the crankshaft 72 to the water pump 8 has been described. The present invention is not limited to this, and can also be applied to a clutch device disposed between another auxiliary machine such as an oil pump and a compressor and the crankshaft 72. The present invention is not limited to switching the transmission state of power from the crankshaft 72 but may be applied as a clutch device that switches the transmission state of power from another power source.

  The present invention can be applied to a clutch device that switches between an engaged state where engine power is transmitted to a water pump and a disengaged state where engine power is not transmitted.

DESCRIPTION OF SYMBOLS 1 Clutch apparatus 3 Clutch mechanism 4 Drive side rotary body 5 Driven side rotary body 57 Inclined groove 57a Side surface 57aII Inclined side surface 58 Linear groove 58a Side surface 61 Locking member 66 Protruding part 69 Pin 9 Pin insertion limiting mechanism 92b Eccentric cam (regulating member) )

Claims (1)

An inclined side surface that is movable between a connection position connected to the drive-side rotator and a connection release position where the connection is released, and is inclined toward one side in the axial direction with respect to the circumferential direction. A driven-side rotating body including an inclined groove, and a linear groove having a side surface provided adjacent to the inclined groove and extending in a direction orthogonal to the axial direction;
A locking member insertable into the inclined groove of the driven side rotating body,
When the locking member is inserted into the inclined groove of the driven-side rotating body in a state where the driven-side rotating body rotates at the coupling position, the inclined side surface of the inclined groove becomes the locking member. In the clutch device in which the driven-side rotating body moves toward the connection release position along with the rotation, and the engagement member moves from the inclined groove to the linear groove by the contact, and the connection is released. There,
A regulating member that can rotate in synchronization with the rotation of the driven-side rotating body and has an outer surface with an unequal length from the rotation axis is disposed on the outer peripheral side of the inclined groove of the driven-side rotating body. Provided,
When the locking member faces a predetermined insertion restriction request region in the forming range of the inclined side surface in the inclined groove, an interference outer surface having a long distance from the rotation axis in the restricting member is formed. While the insertion of the locking member into the inclined groove is restricted by interfering with the locking member,
When the locking member faces a predetermined insertion request region that is a region other than the forming range of the inclined side surface in the inclined groove, the distance from the rotation axis of the restricting member is short. The clutch device is configured such that the non-interfering outer surface faces the locking member so as not to interfere with the locking member and the insertion of the locking member into the inclined groove is allowed.

Images