JP2015081679A - Clutch device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a clutch device for allowing a locking member for maintaining a release state to move surely.SOLUTION: A driven-side rotor 5 is advanced to a drive-side rotor 4 and a clutch device 1 is made in an engagement state by a ball lock mechanism. A spiral groove 57 is formed on an outer peripheral surface of the driven-side rotor 5, a pin 69 of a locking member 61 is inserted into the spiral groove 57 to bring a side 57a of the spiral groove 57 into contact with the pin 69 when the driven-side rotor 5 is in an advanced position. As a result, the driven-side rotor 5 is moved backward with its rotation to make the clutch device 1 in a release state. A guide groove 9 for guiding a movement locus of the pin 69 is provided on the side 57a of the spiral groove 57, and the pin 69 is guided toward a bottom face 58b of an annular groove 58 and automatically inserted into the annular groove 58 if the driven-side rotor 5 rotates while the pin 69 is locked in the guide groove 9.

Description

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

  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 rotating body linked to a crankshaft and a driven side rotating body linked to a water pump, and these rotating bodies are engaged by press-contacting using a magnetic force. A clutch device that is in a state is disclosed. Specifically, the clutch device disclosed in Patent Document 1 includes a magnet that imparts a magnetic force directed to the drive-side rotator to the driven-side rotator, and a coil that cancels the magnetic field of the magnet when energized. ing. When the coil is not energized, the driving-side rotator and the driven-side rotator are brought into pressure 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 present patent applicant 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 rotating body (Japanese Patent Application Nos. 2012-211046 and 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 toward the driving side rotator to the driven side rotator is provided. Further, as shown in FIG. 13A (view of the driven-side rotator a seen from the direction along the axis), the spiral groove b and the annular groove c are adjacent to each other on the outer peripheral surface of the driven-side rotator a. And a locking member d that can be inserted into the spiral groove b. The bottom surface c1 of the annular groove c is located on the inner peripheral side with respect to the bottom surface b1 of the spiral groove b. In a state where the locking member d is not inserted into the spiral groove b, the driven-side rotator a moves forward toward the drive-side rotator by the urging force of the urging means, and these rotators are connected to each other. Thus, the clutch device is engaged. On the other hand, as shown in FIG. 13A and FIG. 13B (cross-sectional view showing the grooves b and c and the locking member d; cross-sectional view along the line BB in FIG. 13A), When the locking member d is inserted into the spiral groove b, the rotational force of the driven-side rotating body a causes the driven-side rotating body a to be pivoted due to the contact between the locking member d and the side wall b2 of the spiral groove b. It is converted into the force to slide along. As a result, the driven side rotating body a moves backward from the driving side rotating body while rotating. When the rotation of the driven side rotating body a further proceeds, FIG. 14 (FIG. 14 (a) is a view of the driven side rotating body a seen from the direction along the axis, and FIG. 14 (b) is an annular groove. As shown in a cross-sectional view showing the c and the locking member d (a cross-sectional view taken along the line BB in FIG. 14A), the locking member d is detached from the spiral groove b, so that the annular groove is formed. It moves to the inner peripheral side toward c (pressed into the annular groove c), and the clutch device is released. When the locking member d moves to the annular groove c in this way, the locking member d and the side wall c2 of the annular groove c come into contact with each other, and the forward / backward movement of the driven side rotating body a is restricted, whereby the clutch device. The released state is maintained.

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 locking member is inserted into the spiral groove and the driven-side rotator is retracted to the position where the clutch device is released, the locking member is reliably moved from the spiral groove to the annular groove (the locking member is It has been noted that it is necessary to ensure that it can be inserted into the annular groove. In particular, when the rotational speed of the driven rotating body is high, it is difficult to move the locking member to the annular groove. Even in such a case, the movement of the locking member from the spiral groove to the annular groove is ensured. The inventors of the present invention paid attention to the fact that it is necessary to ensure the reliability of the operation of the clutch device.

  The present invention has been made in view of such points, and an object of the present invention is to provide a clutch device capable of reliably moving a locking member for maintaining a released state. .

-Solution principle of the invention-
The solution principle of the present invention devised to achieve the above object is that the spiral groove is provided on the side surface of the spiral groove with a guide function for guiding the locking member toward the annular groove toward the inner peripheral side. The inserted locking member is reliably guided to the annular groove by this guide function.

-Solution-
Specifically, the present invention provides a driven-side rotating body that receives power from a power generation source, a driven position that is movable between a connecting position connected to the driving-side rotating body and a release position where the connection is released. A side rotary body, a spiral groove provided in the driven side rotary body, an annular groove provided adjacent to the spiral groove, and a locking member insertable into the spiral groove, the driven side rotation When the locking member is inserted into the spiral groove in a state where the body is in the coupling position, the driven rotary body is moved by the contact between the inclined side surface provided in the spiral groove and the locking member. The present invention is directed to a clutch device that moves toward the release position with rotation, and then holds the driven rotary body in the release position by inserting the locking member into the annular groove. The clutch device is provided with an engaging portion that engages the inserted locking member so as not to be detached in the spiral groove. And by extending this engaging part toward the said annular groove, the latching member which moves relatively along the extension direction of the said engaging part with rotation of a driven side rotary body is guided to the said annular groove. It is configured.

  Due to this specific matter, when the locking member is inserted into the spiral groove in a state where the driven-side rotator is in the coupling position, the locking member cannot be detached from the engaging portion as the driven-side rotator rotates. Combined. Since the engaging portion extends toward the annular groove, the locking member is relatively moved along the extending direction of the engaging portion and guided toward the annular groove as the rotation of the driven side rotating body proceeds. become. Thus, the locking member inserted into the spiral groove is automatically guided to the annular groove, and the locking member can be reliably moved from the spiral groove to the annular groove.

  In the present invention, the locking member inserted in the spiral groove is relatively moved along the extending direction of the engaging portion in accordance with the rotation of the driven side rotating body, and is guided to the annular groove. For this reason, the locking member can be reliably moved from the spiral groove to the annular groove, and the reliability of the operation of the clutch device can be improved.

It is sectional drawing of the clutch apparatus which concerns on embodiment. It is a perspective view of a driven side rotary body. It is a side view which shows the releasing state of a clutch apparatus. It is a side view which shows the engagement state of a clutch apparatus. FIG. 5 is a cross-sectional view at a position corresponding to a line VV in FIG. 3 in a state where the locking member is inserted into the spiral groove. It is a figure which expand | deploys and shows each of the spiral groove formation area and annular groove formation area of the driven side rotary body in 1st Embodiment. It is a perspective view which expand | deploys and shows the spiral groove formation area in 1st Embodiment. It is sectional drawing which shows the change of the engagement state of the groove | channel and a pin in 1st Embodiment. It is sectional drawing which shows the change of the engagement state of the groove | channel and a pin in the modification of 1st Embodiment. It is a perspective view which expands and shows a spiral groove formation field in a 2nd embodiment. It is sectional drawing which shows the change of the engagement state of the groove | channel and a pin in 2nd Embodiment. It is sectional drawing which shows the change of the engagement state of the groove | channel and a pin in the modification of 2nd Embodiment. FIG. 13A shows a state in which the locking member is inserted in the spiral groove, FIG. 13A is a view of the driven side rotating body viewed from the direction along the axis, and FIG. It is sectional drawing which shows a member FIG. 14A shows a state in which the locking member is inserted into the annular groove, FIG. 14A is a view of the driven-side rotating body viewed from the direction along the axis, and FIG. 14B shows the annular groove and the locking member. It is sectional drawing which shows a member

  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 rotator 5 is supported on the clutch output shaft 11 by spline fitting so that the driven-side rotator 5 can 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 receiving recess 52b of the driven side rotating body 5. Thereby, the driven side rotating body 5 is urged toward the driving side rotating body 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 recess 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 (for example, three) of extended portions 51a, 51a, 51a extending toward the concave portion 41 of the drive-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 54 extends along the axial direction of the driven-side rotator 5. The connecting groove portion 55 extends along the circumferential direction of the driven-side rotator 5 from one end of the connection releasing groove portion 54 (one end near the small diameter portion 52). 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 this drive side rotary body 4 and the spherical body accommodation groove | channel 53 of the said driven side rotary body 5 have faced. 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 moves in the axial direction between a position approaching the drive-side rotator 4 (position shown in FIG. 4) and a position retreating from the drive-side rotator 4 (position shown in FIG. 3). It is possible to move forward and backward (slide movement) along.

  As shown in FIG. 4 (a side view showing the engaged state of the clutch device 1), when the driven-side rotator 5 moves to a position approaching the drive-side rotator 4 by the urging force of the urging 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 between the inner peripheral surface of the concave portion 41 of the drive-side rotator 4 and the outer peripheral surface of the large-diameter portion 51 of the driven-side rotator 5, the depth of the connecting groove 55, and the arc groove 42. The total sum of these and the depth dimension is slightly smaller than the outer diameter dimension of the sphere 31. Therefore, as shown in FIG. 4, 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. . In other words, 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. It 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 as the driven-side rotator 5 rotates, and cooling water is discharged from the water pump 8. Hereinafter, the position (sliding movement position along the axial center) of the driven-side rotator 5 in a state where the drive-side rotator 4 and the driven-side rotator 5 are connected is referred to as a lock position (a connecting position in the present invention). Call it.

  On the other hand, as shown in FIG. 3 (a side view showing the released state of the clutch device 1), the driven-side rotator 5 moves to a position where it is retracted from the drive-side rotator 4 against the urging force of the urging member SP. In this case, 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 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 connection release groove portion 54, and the arc groove The sum total with the depth dimension of 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. 3, 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 spherical body 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. Hereinafter, the position (sliding movement position along the axis) of the driven-side rotator 5 in a state where the connection between the drive-side rotator 4 and the driven-side rotator 5 is released is referred to as an unlock position (in the present invention). This is called the 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 rotator 4 and the driven-side rotator 5 are connected to each other (the engaged state of the clutch device 1) by moving the driven-side rotator 5 forward toward the drive-side rotator 4 to the locked position. Become. On the other hand, the driven-side rotator 4 and the driven-side rotator 5 are in a disconnected state (the clutch device 1 is released) by retracting the driven-side rotator 5 from the drive-side rotator 4 to the unlock position. .

  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 advancing / retreating mechanism 32 has a locking unit 6 having a groove 56 formed on the outer peripheral surface of the driven-side rotating body 5 and a locking member 61 inserted into the groove 56. It has. 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 rotator 5. The groove 56 is orthogonal to the spiral groove 57 having an inclined side surface 57aII (see FIG. 6) extending in a direction inclined by a predetermined angle with respect to the circumferential direction (direction orthogonal to the axial direction). And an annular groove 58 having a side surface 58a extending in the direction in which it extends. As for the arrangement positions of the spiral groove 57 and the annular groove 58, the annular groove 58 is closer to the large-diameter portion 51 than the spiral groove 57.

  The spiral groove 57 has a side surface 57a (having a pin insertion side surface 57aI and an inclined side surface 57aII described later; see FIG. 6) extending in the radial direction, and an axial center from the inner peripheral end of the side surface 57a toward the annular groove 58 side. And a bottom surface 57b extending in the direction along. Further, a guide structure for guiding a movement locus of a pin 69 (described later) provided in the locking member 61 is provided on the side surface 57 a of the spiral groove 57. Details of the guide structure will be described later.

  FIG. 6 shows a region in which the spiral groove 57 is formed in the small diameter portion 52 of the driven-side rotating body 5 (hereinafter referred to as a spiral groove forming region) and a region in which the annular groove 58 is formed (hereinafter referred to as an annular groove forming region). It is a figure which expands and shows each. In FIG. 6, the left-right direction is the circumferential direction of the small diameter portion 52, and the vertical direction is the axial direction of the small diameter portion 52. As shown in FIG. 6, on the outer peripheral surface of the small diameter portion 52, a spiral groove forming region and an annular groove forming region extending in the circumferential direction are provided adjacent to each other.

  The predetermined range in the circumferential direction of the side surface 57a in the spiral groove forming region is the rotational direction of the driving side rotating body 4 (the rotational direction of the driven side rotating body 5 when the clutch device 1 is in the engaged state. Then, it may gradually approach the annular groove 58 so as to gradually approach the drive-side rotor 4 toward the upstream side (which may be referred to as the rotational direction of the driven-side rotor 5) (toward the right direction in FIG. 6). (Ii) The inclined side surface 57aII is inclined. In FIG. 6, since the inclined side surface 57aII is hidden by the guide structure of the pin 69 (protrusion 91 described later), the inclined side surface 57aII is represented by a broken line. 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 the total perimeter length of the small-diameter portion 52 of the driven side rotating body 5 and the movement required for the driven side rotating body 5. It is set as appropriate according to the amount (the amount of movement between the lock position and the unlock 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.

  Since the inclined side surface 57aII is formed in this way, in the range t2 where the inclined side surface 57aII is provided, the width dimension (dimension in the direction along the axis) of the bottom surface 57b extends in the circumferential direction. (Toward the upstream side in the rotational direction of the driven-side rotator 5).

  Further, a pin insertion side surface 57aI extending in a direction orthogonal to the axial direction (not inclined) is provided downstream of the inclined side surface 57aII in the rotation direction of the driven side rotator 5 (left side in FIG. 6). 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 spiral groove 57 is not formed on the upstream side (the right side in FIG. 6) in the rotational direction of the driven-side rotator 5 with respect to the inclined side surface 57aII, and this region is the outer peripheral surface and the surface of the small-diameter portion 52. One circular arc surface 57aIII (the outer diameter of the small-diameter portion 52 and the dimension in the radial direction coincide with each other) is formed.

  The portion where the pin insertion side surface 57 a I 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 spiral groove 57. Hereinafter, this region is referred to as a start end portion 57c. In the spiral groove 57 having the shape shown in FIG. 6, the range t3 in the above-described drawing is the formation range of the pin insertion side surface 57aI constituting the start end portion 57c. The upstream end of the inclined side surface 57aII in the rotational direction of the driven-side rotator 5 corresponds to a position where the pin 69 is detached from the spiral groove 57. Hereinafter, this portion is referred to as a termination portion 57d.

  Further, as the depth dimension of the spiral 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 spiral groove 57 is constant over the entire circumference (FIG. 5 (a cross section at a position corresponding to the line VV in FIG. 3). (See the depth of the spiral groove 57 shown in the figure).

  On the other hand, the annular groove 58 is formed over the entire circumference of the outer peripheral surface of the driven-side rotator 5 adjacent to the spiral groove 57. The annular 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 side. The entire side surface 58a is a plane perpendicular to the axis. That is, the side surface 58a is not inclined. In FIG. 6, a part of the side surface 58 a is hidden by the guide structure of the pin 69 (protrusion 91 described later), and therefore the side surface 58 a is represented by a broken line in this portion. Further, the bottom surface 58 b is located on the inner peripheral side with respect to the bottom surface 57 b of the spiral groove 57. That is, the depth dimension of the annular groove 58 is larger than the depth dimension of the spiral groove 57. For this reason, the annular groove 58 and the spiral groove 57 are adjacent to each other with a step between them. Further, in the annular groove 58, a position adjacent to the terminal end portion 57d of the spiral groove 57 is a start end portion 58c where insertion of the pin 69 is started.

  Thus, the spiral groove 57 and the annular groove 58 are formed, so that the driven-side rotating body 5 is in the locked position as shown in FIG. In the connected state, when the locking member 61 rotates toward the groove 56, the pin 69 of the locking member 61 is moved to the start end portion 57c (pin insertion side surface 57aI of the spiral groove 57). Is inserted into the spiral groove 57. When the pin 69 is thus inserted into the spiral groove 57, the driven-side rotator 5 rotates with the inclined side surface 57 a II of the spiral groove 57 in contact with the pin 69. Then, while the inclined side surface 57aII of the spiral groove 57 slides on the pin 69, the driven-side rotator 5 moves in the direction along the axis (rightward in FIG. 4) from the lock position toward the unlock position. As the driven-side rotator 5 moves, the spherical body 31 relatively moves from the connecting groove portion 55 provided in the driven-side rotator 5 toward the connection releasing groove portion 54.

  When the pin 69 reaches the terminal end portion 57 d of the spiral groove 57, the pin 69 starts moving from the start end portion 58 c of the annular groove 58 toward the annular groove 58. The movement of the pin 69 into the annular groove 58 is realized by the guide structure of the pin 69. The movement operation of the pin 69 by this guide structure will be described later. 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 spiral 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. 5, 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 front end side (the upper end side in FIG. 5) 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. 5) faces the fixed core 64b, while the distal end (the upper side in FIG. 5). 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 a solid line in FIG. 5, the degree to which the movable core 64 c protrudes from the second case 65 by the urging force of the coil spring 65 c increases, so that the pin 69 of the locking member 61 is connected to the driven side rotating body 5. It is 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 the 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. 5), the locking member 61 rotates counterclockwise in FIG. 5, 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 (position indicated by a virtual line in FIG. 5), 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 attracted when the movable core 64c is in the contact position indicated by the phantom line in FIG. 5, what is the direction of the magnetic field of the permanent magnet 65a? A reverse magnetic field is generated. Thereby, the attractive force of the permanent magnet 65a is weakened, and the movable core 64c is separated from the fixed core 64b by the biasing force of the coil spring 65c, and moves 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. 5 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 guide structure)
Next, a plurality of embodiments of the guide structure that guides the movement of the pin 69, which is a feature of this embodiment, will be described.

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

  FIG. 7 is an exploded perspective view showing the spiral groove forming region in the present embodiment. FIG. 8 is a cross-sectional view showing a change in the engagement state between the groove 56 and the pin 69 in the present embodiment. Specifically, FIG. 8A is a cross-sectional view showing a case where the pin 69 is in an initial state inserted into the spiral groove 57 and the driven-side rotator 5 is in the position shown in FIG. FIG. 8B shows a state in which the pin 69 is inserted into the spiral groove 57 and the relative position of the pin 69 with respect to the driven side rotating body 5 is at the B position shown in FIGS. 5 and 6 (driven side rotation). FIG. 6 is a cross-sectional view showing a case where the body 5 is rotated about 180 ° from the position shown in FIG. 5. FIG. 8 (c) shows a case where the relative position of the pin 69 with respect to the driven-side rotator 5 is at the position C shown in FIGS. 5 and 6 (the driven-side rotator 5 is rotated about 320 ° from the position shown in FIG. 5). FIG. FIG. 8D shows a state in which the pin 69 is inserted in the annular groove 58, and the relative position of the pin 69 with respect to the driven side rotating body 5 is at the D position shown in FIGS. 5 and 6 (driven side rotation). FIG. 6 is a cross-sectional view showing a case where the body 5 is rotated about 360 ° from the position shown in FIG. 5.

  As shown in these drawings, the relative position of the pin 69 (relative position in the radial direction) with respect to the driven-side rotating body 5 is regulated on the inclined side surface 57aII of the spiral groove 57 and a part of the side surface 58a of the annular groove 58. A guide groove (engagement portion) 9 for guiding the pin 69 is formed.

  The guide groove 9 is a groove that is recessed so that the direction along the axis of the driven-side rotator 5 (the direction orthogonal to the paper surface in FIG. 5 and the vertical direction in FIG. 6) is the depth direction. The bottom surface of the guide groove 9 is a surface corresponding to the inclined side surface 57aII. That is, the guide groove 9 has the inclined side surface 57aII as a bottom surface, and is driven to rotate from the outer peripheral side edge (upper edge in FIG. 8) and inner peripheral side edge (lower edge in FIG. 8) of the inclined side surface 57aII. It is formed by a pair of protrusions 91 and 92 protruding along the axis of the body 5 (projecting toward the bottom surface 57b).

  And this guide groove 9 is extended in the circumferential direction of the driven side rotary body 5, and as shown in FIG. 7, the introduction area | region 9A, the axial center inclination area | region 9B, and the radial direction transition area | region 9C along the extension direction. Is continuously provided from the downstream side to the upstream side in the rotational direction of the driven-side rotator 5 (from the left side to the right side in FIG. 7). This will be specifically described below.

  The introduction region 9 </ b> A of the guide groove 9 is a region for introducing the pin 69 of the locking member 61 into the guide groove 9. In the pin 69 of the locking member 61, a small diameter ball 69b is rotatably embedded in the surface of the spiral groove 57 facing the side surface 57a. Therefore, in a state where the pin 69 is engaged with the guide groove 9, the ball 69b is actually fitted into the guide groove 9 (see FIGS. 8A to 8C). In this state, when the driven-side rotating body 5 rotates with respect to the pin 69, the ball 69b rotates to reduce the friction loss with the guide groove 9.

  As shown in FIG. 7, the introduction region 9 </ b> A of the guide groove 9 has a groove width dimension (a dimension in the height direction of the guide groove 9) toward the downstream side (left side in FIG. 7) in the rotational direction of the driven side rotating body 5. ) Is an expanding shape. As a result, the pin 69 (more specifically, the ball 69b embedded in the pin 69) inserted into the start end portion 57c of the spiral groove 57 (the region where the pin insertion side surface 57aI is formed) is moved to the driven side rotating body 5. The guide groove 9 is surely introduced with the rotation.

  The axially inclined region 9B of the guide groove 9 is a region corresponding to a region where the inclined side surface 57aII is provided (range t2 in FIG. 6). That is, in this axially inclined region 9B, the bottom surface (inclined side surface 57aII) of the guide groove 9 is directed toward the upstream side in the rotational direction of the driven-side rotator 5 (to the right in FIG. 7). It inclines so that it may approach gradually (from the back | inner side of the paper surface in FIG. 7 toward this side). As a result, as described above, the driven-side rotating body 5 rotates as the driven-side rotating body 5 rotates while the inclined side surface 57aII (the bottom surface of the guide groove 9) of the spiral groove 57 contacts the pin 69 (ball 69b). It moves in the direction along the axis from the lock position to the unlock position (right direction in FIG. 4).

  The radial transition area 9C of the guide groove 9 is an area provided in the vicinity of the start end portion 58c of the annular groove 58, and as shown in FIGS. It curves toward the inner peripheral side toward the side (toward the right direction in FIG. 7). In other words, each of the pair of protrusions 91 and 92 is curved toward the inner peripheral side, whereby the pin 69 is a region guided to the inner peripheral side (the side toward the bottom surface 58b) of the annular groove 58.

  As described above, in the guide groove 9, the introduction region 9 </ b> A, the axially inclined region 9 </ b> B, and the radial direction transition region 9 </ b> C extend from the downstream side to the upstream side in the rotational direction of the driven side rotating body 5. Therefore, when the ball 69b embedded in the pin 69 is introduced into the guide groove 9 from the introduction region 9A, the rotation of the driven side rotator 5 thereafter proceeds. The ball 69b relatively moves in the order of the introduction region 9A of the guide groove 9, the axially inclined region 9B, and the radial direction transition region 9C. That is, the period during which the ball 69b moves relatively in the axially inclined region 9B while preventing the ball 69b from detaching from the guide groove 9 (while preventing the pin 69 from detaching from the groove 56). Then, the driven-side rotator 5 moves backward from the drive-side rotator 4 and moves toward the unlock position. Then, during the period in which the ball 69b is relatively moving in the radial direction transition region 9C, the ball 69b is guided toward the bottom surface 58b of the annular groove 58 so that the pin 69 is inserted into the annular groove 58. It has become.

-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 the phantom line in FIG. At this time, as shown in FIG. 4, since the driven-side rotator 5 is held in the locked position by the urging force of the urging member SP, the sphere 31 is positioned in the connecting groove 55, and the clutch device 1 is engaged. It is in a joint 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.

  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. 5, the pin 69 of the locking member 61 has its start end portion 57 c with respect to the spiral groove 57 in the groove 56 of the driven side rotating body 5. It is inserted from (region where the pin insertion side surface 57aI is formed). At this time, when the pin 69 of the locking member 61 moves toward a region other than the start end portion 57c of the spiral groove 57, the pin 69 comes into contact with the outer peripheral surface of the small diameter portion 52, and thereafter When the start end portion 57c of the spiral groove 57 reaches a position facing the pin 69 as the driven side rotating body 5 rotates, the pin 69 is inserted into the spiral groove 57 from the start end portion 57c. .

  After the pin 69 is inserted into the spiral groove 57, the rotation of the driven-side rotator 5 advances the ball 69b of the pin 69 from the introduction region 9A to the guide groove 9 (see FIG. 8A). . When the ball 69b is introduced into the guide groove 9 in this way, the protrusion 91 of the guide groove 9 is positioned on the outer peripheral side of the ball 69b, so that the ball 69b does not come out of the guide groove 9. That is, the rotation of the driven-side rotator 5 proceeds with the ball 69 b fitted in the guide groove 9, so the position of the pin 69 (the radial position of the driven-side rotator 5) is regulated by the guide groove 9. It will be. That is, the locus of the pin 69 is guided by the guide groove 9.

  When the ball 69b reaches the axially inclined region 9B of the guide groove 9 along with the rotation of the driven side rotating body 5, while the ball 69b relatively moves in the guide groove 9, the driven side rotating body With the rotation of 5, the driven-side rotator 5 moves from the lock position toward the unlock position (see FIG. 8B). That is, the state changes from the state shown in FIG. 4 to the state shown in FIG.

  Thereafter, when the rotation of the driven-side rotator 5 proceeds, the ball 69b reaches the radial direction transition region 9C of the guide groove 9. As described above, the radial direction transition region 9C is curved toward the inner peripheral side. For this reason, when the ball 69b moves along the radial direction transition region 9C, the pin 69 is guided to the inner peripheral side (side toward the bottom surface 58b) of the annular groove 58 (see FIG. 8C). Further, when the rotation of the driven-side rotator 5 advances and the ball 69b reaches a region where the guide groove 9 is not provided (side surface 58a of the annular groove 58), the restriction of the ball 69b by the guide groove 9 is released. (See FIG. 8D). At this time, the pin 69 has already reached the bottom surface 58b of the annular groove 58 and is inserted into the annular 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. It becomes a state.

  Immediately after the connection between the driven-side rotator 5 and the drive-side rotator 4 is released, the driven-side rotator 5 has the pin 69 inserted in the annular groove 58 as shown in FIG. 69, while continuing the rotation by the inertial force while receiving the action of the frictional force generated between the two. When the pin 69 is inserted into the annular groove 58 in this way, the pin 69 is engaged with the step existing at the boundary between the spiral groove 57 and the annular groove 58, that is, the side surface 58 a of the annular groove 58. Therefore, as long as the pin 69 is displaced so as to be pulled out from the annular groove 58 and does not get over this step, the pin 69 is not displaced into the spiral groove 57. Thus, in the state where the pin 69 of the locking member 61 is inserted into the annular 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. 5 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 coupled. The clutch device 1 is switched to the engaged state.

  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 this embodiment, the guide groove 9 for guiding the pin 69 is formed in the inclined side surface 57aII of the spiral groove 57 and a part of the side surface 58a of the annular groove 58. And then. The radial transition region 9C of the guide groove 9 guides the pin 69 toward the bottom surface 58b of the annular groove 58. For this reason, the pin 69 inserted into the spiral groove 57 can be automatically guided to the annular groove 58, and the pin 69 can be reliably moved from the spiral groove 57 to the annular groove 58. As a result, the reliability of the operation of the clutch device 1 can be improved. Further, it is possible to avoid a situation in which the pin 69 cannot be moved to the annular groove 58 and the pin 69 continuously slides on the inclined side surface 57aII of the spiral groove 57. For this reason, the contact load generated between the pin 69 and the inclined side surface 57aII can be reduced, and the wear of the pin 69 can be suppressed.

  Further, in the configuration without the guide groove 9, when the pin 69 is moved from the spiral groove 57 to the annular groove 58, an electromagnetic force for pushing the pin 69 to the bottom surface 58 b of the annular groove 58 is used. Need to be generated. On the other hand, when the pin 69 inserted into the spiral groove 57 can be automatically guided to the annular groove 58 by the guide groove 9 as in this embodiment, the electromagnetic force generated by the actuator 62 is small. It is possible to reduce power consumption.

<Modification of First Embodiment>
Next, a modification of the first embodiment will be described. In this example, the shape of the guide groove is different from that of the first embodiment described above. Here, only the difference (the shape of the guide groove) from the first embodiment will be described.

  FIG. 9 is a cross-sectional view showing a change in the engagement state between the groove 56 and the pin 69 in this example. Specifically, FIG. 9A is shown in FIG. 8A, FIG. 9B is shown in FIG. 8B, FIG. 9C is shown in FIG. 8C, and FIG. It is a figure corresponding to 8 (d), respectively.

  As shown in these drawings, the guide groove 9 in this example is provided on the inclined side surface 57aII of the spiral groove 57 and a part of the side surface 58a of the annular groove 58, and is on the axial center side (FIG. 9). It is formed with the inclined surface 93 which inclines to the water pump 8 side (right side in FIG. 9) as it goes to the lower side. The formation range of the guide groove 9 is the same as that of the first embodiment. The guide groove 9 also has an introduction region 9A, an axially inclined region 9B, and a radial direction transition region 9C, as in the first embodiment.

  Even in the guide groove 9 having such a shape, when the ball 69b is introduced into the guide groove 9, the ball 69b is prevented from being detached from the guide groove 9 (the pin 69 is detached from the groove 56). The ball 69b is relatively moved along the guide groove 9 while preventing this). Thereby, the same effect as the case of 1st Embodiment mentioned above can be acquired.

Second Embodiment
Next, a second embodiment of the guide structure of the pin 69 will be described. In the present embodiment, the formation range of the guide groove 9 (formation range in the circumferential direction of the driven-side rotating body 5) is different from that of the first embodiment described above. Here, only the difference (formation range of the guide groove 9) from the first embodiment will be described.

  FIG. 10 is an exploded perspective view showing the spiral groove forming region in the present embodiment. FIG. 11 is a cross-sectional view showing a change in the engagement state between the groove 56 and the pin 69 in the present embodiment. Specifically, FIG. 11A is shown in FIG. 8A, FIG. 11B is shown in FIG. 8B, FIG. 11C is shown in FIG. 8C, and FIG. It is a figure corresponding to 8 (d), respectively.

  As shown in these drawings, the guide groove 9 in the present embodiment includes a pin holding region 9D in addition to the introduction region 9A, the axially inclined region 9B, and the radial direction transition region 9C. The cross-sectional shape of the guide groove 9 is the same as that of the first embodiment.

  Further, the pin 69 in the present embodiment has a protrusion 69c instead of the ball 69b.

  The pin holding region 9D is provided on the side surface 58a of the annular groove 58, and holds the projection 69c in a state where the pin 69 is inserted into the annular groove 58 (projection in the radial direction of the driven side rotating body 5). 69c), which is continuous with the radial direction transition region 9C and extends upstream in the rotational direction of the driven-side rotator 5.

  Thereby, the state in which the pin 69 is inserted into the annular groove 58 can be reliably held.

  Further, the pin holding region 9 </ b> D is not provided in a part of the side surface 58 a of the annular groove 58. For this reason, when the pin 69 is pulled out from the annular groove 58 in order to switch the clutch device 1 from the released state to the engaged state, it can be pulled out from a portion where the pin holding region 9D is not provided.

<Modification of Second Embodiment>
Next, a modification of the second embodiment will be described. In this example, the shape of the guide groove is different from that of the second embodiment described above. Here, only the difference (the shape of the guide groove) from the second embodiment will be described.

  FIG. 12 is a cross-sectional view showing a change in the engagement state between the groove 56 and the pin 69 in this example. Specifically, FIG. 12A is shown in FIG. 11A, FIG. 12B is shown in FIG. 11B, FIG. 12C is shown in FIG. 11C, and FIG. It is a figure corresponding to 11 (d), respectively.

  As shown in these drawings, the guide groove 9 in this example is provided from the inclined side surface 57aII of the spiral groove 57 to the side surface 58a of the annular groove 58, and is on the axial center side (in FIG. 9). It is formed with an inclined surface 93 that is inclined toward the water pump 8 side (right side in FIG. 12) as it goes toward the lower side. The formation range of the guide groove 9 is the same as that of the second embodiment. The guide groove 9 also has an introduction region 9A, an axially inclined region 9B, a radial direction transition region 9C, and a pin holding region 9D, as in the second embodiment.

  Even in the guide groove 9 having such a shape, when the protrusion 69c is introduced into the guide groove 9, the protrusion 69c is prevented from being detached from the guide groove 9 (the pin 69 is detached from the groove 56). While preventing this, the protrusion 69c moves relatively along the guide groove 9. Thereby, the same effect as the case of 2nd Embodiment mentioned above can be acquired.

(Other embodiments)
In each embodiment and each modification described above, the groove depth in the formation range t2 of the inclined side surface 57aII of the spiral groove 57 is uniform in 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 and modifications, the depth of the annular groove 58 is constant over the entire periphery. The present invention is not limited to this, and the groove depth of the start end portion 58c in the annular groove 58 may be shallower than the groove depth of other portions.

  Further, in each of the above-described embodiments and modifications, the groove 56 (the spiral groove 57 and the annular groove 58) into which the pin 69 of the locking member 61 is inserted is provided on the outer peripheral surface of the driven-side rotator 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 so that 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.

  In each of the above embodiments and modifications, the pin 69 of the locking member 61 has a convex portion (the ball 69b or the protrusion 69c), and the groove 56 of the driven-side rotating body 5 has a concave portion (the guide groove 9). However, the pin 69 of the locking member 61 is provided with a recess, the groove 56 of the driven rotor 5 is provided with a protrusion, and the protrusion is inserted into the recess to guide the locus of the pin 69. Also good.

  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 rotator 5 toward the lock position may be applied as the urging 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-described embodiments and modifications, 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 Spiral groove 57a Side surface 57aII Inclined side surface 58 Annular groove 61 Locking member 69 Pin 9 Guide groove (engagement part)

Claims (1)

A driving side rotating body that receives power from a power generation source;
A driven-side rotator movable between a connection position connected to the drive-side rotator and a release position where the connection is released;
A spiral groove provided in the driven side rotating body;
An annular groove provided adjacent to the spiral groove;
A locking member insertable into the spiral groove,
When the locking member is inserted into the spiral groove in a state where the driven-side rotating body is in the coupling position, the driven side is brought into contact with the inclined side surface provided in the spiral groove and the locking member. A clutch device in which a rotating body moves toward the release position along with its rotation, and then the driven member is held in the release position by inserting the locking member into the annular groove. ,
The spiral groove is provided with an engaging portion that detachably engages the inserted locking member, and this engaging portion extends toward the annular groove so that the driven side rotating body can be rotated. Accordingly, the clutch device is configured such that a locking member that relatively moves along the extending direction of the engaging portion is guided by the annular groove.

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