JP2015200362A - clutch device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a clutch device capable of improving dependability when an engaging member is inserted and discharged.SOLUTION: A clutch device 1 is constituted in such a way that, when an engaging member 61 is inserted into an inclined groove 57 of a driven side rotary body 5 by a rotary mechanism 90 in a state in which the driven side rotary body 5 is set at a connected position, the inclined groove 57 is abutted against the engaging member 61 to cause the driven side rotary body 5 to be moved toward its released position as it is rotated. Then, the rotary mechanism 90 comprises a motor 91, a worm 91a, and a worm wheel 92 for amplifying an output torque of the motor 91, and a connecting member 94 connected to the engaging member 61. The output torque of the motor 91 is amplified and transmitted to the connecting member 94 to cause the engaging member 61 to be rotated.

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. In addition, an urging member that causes the urging force directed to the driving side rotator to act on the driven side rotator is provided. In addition, an inclined groove and an annular 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 in which the locking member is not inserted into the inclined groove, the driven-side rotator moves forward toward the drive-side rotator by the urging force of the urging member, and the rotators are connected to each other to connect the clutch 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 converted into a force for sliding the driven-side rotator by the contact between the locking member and the side surface of the inclined groove. The As a result, the driven-side rotator rotates while retreating from the drive-side rotator, the rotators are separated from each other, and the clutch device is released. Then, when the rotation of the driven side rotating body further proceeds and the locking member moves from the inclined groove to the annular groove, the locking member and the side surface of the annular 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 rotator.

JP 2010-203406 A

  Here, in the clutch device described above, a solenoid actuator is provided to rotate the locking member. The locking member is inserted into the inclined groove by the biasing force of the return spring of the solenoid actuator, and the locking member is ejected (pulled out) from the annular groove by the electromagnetic force of the solenoid actuator. Since this solenoid actuator is a self-holding type and does not need to be energized except when driving (inserting and discharging) the locking member, it is possible to reduce power consumption.

  However, when a solenoid actuator is used to rotate the locking member, it is difficult to increase the force for inserting and discharging the locking member. It is difficult to improve the certainty.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a clutch device capable of improving the reliability when the locking member is inserted and discharged. It is.

  The clutch device according to the present invention is provided so as to be movable between a drive-side rotator, a connection position connected to the drive-side rotator, and a release position where the connection is released, and a driven side in which an inclined groove is formed. A rotating body; a biasing member that biases the driven-side rotating body toward the coupling position; a locking member that can be inserted into the inclined groove of the driven-side rotating body; and a rotation mechanism that rotates the locking member. Prepare. The clutch device is configured such that when the locking member is inserted into the inclined groove of the driven side rotating body by the rotation mechanism portion in a state where the driven side rotating body is in the coupling position, the inclined groove contacts the locking member. The driven-side rotator is configured to move toward the release position along with the rotation. The rotation mechanism unit includes a motor, a reduction gear that amplifies the output torque of the motor, and a connecting member that is connected to the locking member, and the output torque of the motor is amplified by the reduction device and transmitted to the connecting member. By doing so, the locking member is configured to be rotated.

  By configuring in this way, the locking member is rotated (inserted and ejected) by the output torque of the motor, so that the locking member is compared with the case where a solenoid actuator is used to rotate the locking member. Since the force for inserting and discharging can be increased, it is possible to improve the reliability when the locking member is inserted and discharged. Further, by providing the reduction gear, it is possible to reduce the size of the motor while increasing the output torque.

  According to the clutch device of the present invention, it is possible to improve the reliability when the locking member is inserted and discharged.

It is sectional drawing which showed the clutch apparatus by 1st Embodiment of this invention. It is the perspective view which showed the driven side rotary body of the clutch apparatus. It is the side view which showed the engagement state of the clutch apparatus. It is the side view which showed the releasing state of the clutch apparatus. It is the figure which expand | deployed and showed each of the inclined groove formation area and annular groove formation area of a driven side rotary body. It is the figure which showed the latching unit when a clutch apparatus is an engagement state. It is the figure which showed the latching unit when a clutch apparatus is a releasing state. It is the figure which showed the latching unit when the clutch apparatus by 2nd Embodiment of this invention is an engagement state. It is the figure which showed the latching unit when the clutch apparatus of FIG. 8 is a releasing state.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Below, the case where the clutch apparatus which concerns on this invention is applied to the water pump with which the cooling system of the engine (internal combustion engine) for motor vehicles was provided is demonstrated. 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.

-First embodiment-
FIG. 1 is a cross-sectional view of the clutch device 1 according to the first 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 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 (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. 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. . 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 axis) 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. 4 (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. 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 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 includes a groove 56 formed on the outer peripheral surface of the driven-side rotating body 5 and a locking unit 6 having a locking member 61 that can be 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 includes an inclined groove 57 having a 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 an annular groove 58 having a side surface 58a extending in a direction orthogonal to the central direction. As the arrangement positions of the inclined grooves 57 and the annular grooves 58, the annular grooves 58 are closer to the large-diameter portion 51 than the inclined grooves 57.

  The inclined groove 57 includes a side surface 57a extending in a radial direction (a pin insertion side surface 57aI described later and a side surface 57aII inclined (inclined by a predetermined angle with respect to the circumferential direction); see FIG. 5). And a bottom surface 57b extending in the direction along the axial center from the inner peripheral end of 57a toward the annular 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 rotator 5 (hereinafter referred to as an inclined groove forming region) and a region where 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. 5, 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. 5, an inclined groove forming region and an annular groove forming region are provided adjacent to each other on the outer peripheral surface of the small diameter portion 52 in the circumferential direction.

  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 rotator 4 (the rotational direction of the driven side rotator 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. 5). B) the inclined side surface 57aII. The inclination angle and inclination range of the side surface 57aII (the angular range in the circumferential direction in which the 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 amount of movement required for the driven side rotating body 5 ( The amount of movement between the lock position and the unlock position is set as appropriate. 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 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 side surface 57aII is provided is set to a range of 250 °. These values are not limited to this.

  Thus, since the side surface 57aII inclined with respect to the circumferential direction is formed, the width dimension (dimension in the direction along the axis) of the bottom surface 57b is within the range t2 where the side surface 57aII is provided. Further, it gradually narrows 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 on the downstream side (left side in FIG. 5) of the driven side rotator 5 with respect to the side surface 57aII. It has been. 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 (right side in FIG. 5) of the driven-side rotator 5 with respect to the side surface 57aII, and this region is flush with the outer peripheral surface of the small-diameter portion 52. A circular arc surface 57aIII (the outer diameter of the small-diameter portion 52 coincides with the dimension in the radial direction).

  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, at the upstream end in the rotational direction of the driven-side rotator 5 on the side surface 57aII, the pin 69 provided in the locking member 61 of the locking unit 6 is detached from the inclined groove 57 and inserted into the annular groove 58. Corresponds to the insertion start position. Hereinafter, this portion is referred to as a termination portion 57d.

  Further, as the depth dimension of the inclined groove 57, the pin insertion side surface 57aI is gradually deepened toward the side surface 57aII formation range t2 in the formation range t3 of the pin insertion side surface 57aI. Further, in the formation range t2 of the side surface 57aII, the depth dimension of the inclined groove 57 is constant over the entire periphery.

  On the other hand, the annular groove 58 is formed over the entire circumference of the outer peripheral surface of the driven rotary body 5 adjacent to the inclined 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 of the annular groove 58 is a plane perpendicular to the axis. That is, the side surface 58a is not inclined. The bottom surface 58 b of the annular 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 annular groove 58 is larger than the depth dimension of the inclined groove 57. For this reason, the annular groove 58 and the inclined groove 57 are adjacent to each other with a step between them. Further, in the annular groove 58, a position adjacent to the end portion 57d of the inclined groove 57 is a start end portion 58c where the insertion of the pin 69 is started.

  Thus, the inclined 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. When the locking member 61 is rotated toward the groove 56 in the connected state, the pin 69 of the locking member 61 is moved 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. Thus, when the pin 69 is inserted into the inclined groove 57, the driven-side rotator 5 rotates with the side surface 57aII of the inclined groove 57 in contact with the pin 69. Then, while the side surface 57aII of the inclined groove 57 slides on the pin 69, the driven-side rotator 5 moves in the direction along the axis (rightward in FIG. 3) from the locked position toward the unlocked 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 57 d of the inclined groove 57, the pin 69 is inserted into the annular groove 58 from the start end part 58 c of the annular groove 58. That is, the pin 69 is detached from the inclined groove 57 and fitted into the annular 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 side surface 57 a II of the inclined groove 57 to resist the biasing force of the biasing 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.

(Locking unit)
Next, the locking unit 6 will be described with reference to FIGS. 6 and 7.

  The locking unit 6 according to the first embodiment includes a locking member 61 that can be inserted into the groove 56 and a rotation mechanism 90 that rotates the locking member 61. The locking unit 6 switches the clutch device 1 from the engaged state to the released state by sliding the driven-side rotating body 5 from the locked position to the unlocked position against the biasing force of the biasing member SP. Is provided.

  The locking member 61 is provided with a rotation shaft 61a on the base end side, and is configured to be rotatable about the rotation shaft 61a. In addition, the locking member 61 is provided with a pin 69 on the distal end side, and the pin 69 can be inserted into and discharged from the groove 56 of the driven side rotating body 5.

  The rotation mechanism 90 includes a motor 91, a worm wheel 92, a spur gear 93, a connecting member 94, and stoppers 95a and 95b.

  The motor 91 is connected to a control circuit (not shown) and is configured to be able to rotate forward and reverse. A worm 91 a that meshes with the worm wheel 92 is provided on the output shaft of the motor 91. For this reason, the worm 91a and the worm wheel 92 function as a reduction gear (worm gear) that amplifies the output torque of the motor 91.

  The worm wheel 92 is provided so as to be rotatable about a rotation shaft 92a. Further, the worm wheel 92 is provided with a spur gear 92b that rotates integrally around a rotation shaft 92a. The spur gear 92 b is in mesh with the spur gear 93. The spur gear 93 is provided so as to be rotatable about a rotation shaft 93a. The worm wheel 92 and the spur gears 92 b and 93 are rotated by a motor 91.

  The connecting member 94 has one end connected to the spur gear 93 and the other end connected to the locking member 61. The connecting member 94 is provided to convert the rotational motion of the spur gear 93 rotated by the motor 91 into the rotational (swinging) motion of the locking member 61. The stoppers 95a and 95b are provided to restrict the rotation range of the locking member 61. Specifically, the stopper 95a has a function of positioning the locking member 61 when the locking member 61 is ejected from the groove 56, and the stopper 95b has the locking member 61 inserted into the groove 56. Sometimes it has a function of positioning the locking member 61.

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

  First, as shown in FIG. 6, the locking member 61 is discharged from the groove 56 and is in contact with the stopper 95a. At this time, as shown in FIG. 3, 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, as shown in FIG. 6, when the motor 91 is rotated in the forward rotation direction, the worm wheel 92 is rotated clockwise in FIG. At this time, the spur gear 92b is rotated together with the worm wheel 92, and the spur gear 93 meshing with the spur gear 92b is rotated counterclockwise in FIG. Thereby, the connecting member 94 is moved so as to approach the axial center of the driven-side rotator 5, and the pin 69 of the locking member 61 is inserted into the groove 56.

  Specifically, the pin 69 of the locking member 61 is inserted into the inclined groove 57 in the groove 56 of the driven-side rotator 5 from its starting end portion 57c (region where the pin insertion side surface 57aI is formed). At this time, when the pin 69 of the locking member 61 moves toward the region other than the start end portion 57c of the inclined 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 inclined groove 57 reaches a position facing the pin 69 as the driven side rotating body 5 rotates, the pin 69 is inserted into the inclined groove 57 from the start end portion 57c. .

  When the pin 69 is inserted into the inclined groove 57 and the driven side rotating body 5 rotates together with the driving side rotating body 4 with the pin 69 in contact with the side surface 57aII, the pin 69 relatively moves in the inclined groove 57. In the meantime, the driven-side rotator 5 moves from the locked position toward the unlocked position. That is, the state changes from the state shown in FIG. 3 to the state shown in FIG. Thereafter, when the rotation of the driven-side rotator 5 proceeds, the pin 69 is inserted into the annular groove 58 from the terminal end portion 57d of the inclined groove 57 through the start end portion 58c of 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.

  When the pin 69 of the locking member 61 is inserted into the annular groove 58, the locking member 61 comes into contact with the stopper 95b. Then, when the movement of the locking member 61 is restricted by the stopper 95b, energization to the motor 91 is stopped when an increase in the current of the motor 91 due to overload is detected. At this time, since it is difficult to drive the worm 91 a from the worm wheel 92 side, the pin 69 of the locking member 61 is maintained in a state of being inserted into the annular groove 58. That is, while the motor 91 is not energized, the locking member 61 is maintained inserted in the annular groove 58 and the clutch device 1 is maintained in the released 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. In this state, when the pin 69 is inserted into the annular groove 58, the pin 69 is engaged with the step existing at the boundary between the inclined 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 inclined 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, as shown in FIG. 7, the motor 91 is rotated in the reverse direction, and the worm wheel 92 is rotated counterclockwise in FIG. At this time, the spur gear 92b is rotated together with the worm wheel 92, and the spur gear 93 meshing with the spur gear 92b is rotated clockwise in FIG. As a result, the connecting member 94 is moved away from the axis of the driven-side rotator 5, and the pin 69 of the locking member 61 is pulled out (discharged) from the annular groove 58.

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.

  When the pin 69 of the locking member 61 is ejected from the annular groove 58, the locking member 61 comes into contact with the stopper 95a. Then, when the movement of the locking member 61 is restricted by the stopper 95a, energization to the motor 91 is stopped when an increase in the current of the motor 91 due to overload is detected. At this time, since it is difficult to drive the worm 91 a from the worm wheel 92 side, the pin 69 of the locking member 61 is maintained in a state of being discharged from the groove 56. That is, while the motor 91 is not energized, the locking member 61 is maintained in the state of being discharged from the groove 56, and the clutch device 1 is maintained in 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.

(effect)
In the first embodiment, as described above, a solenoid actuator (not shown) is rotated to rotate the locking member 61 by rotating (inserting and discharging) the locking member 61 by the output torque of the motor 91. Compared with the case of using, the force for inserting and discharging the locking member 61 can be increased (for example, 10N or more), so that the reliability when inserting and discharging the locking member 61 is improved. Can do. Further, by providing the worm wheel 92 and the worm 91a on the output shaft of the motor 91, the motor 91 can be reduced in size while increasing the output torque.

  In the first embodiment, since it is difficult to drive the worm 91a from the worm wheel 92 side, the motor is used to maintain the state when the locking member 61 is inserted into and discharged from the groove 56. Since it is not necessary to energize 91, power consumption can be reduced.

  In the first embodiment, a solenoid actuator (in order to rotate the locking member 61 by rotating (swinging) the locking member 61 by the rotation mechanism 90 using the motor 91 as a driving force source). Compared with the case of using a not-shown), the rocking range of the locking member 61 can be widened, so that the degree of freedom in design can be improved.

-Second Embodiment-
Next, with reference to FIG. 8 and FIG. 9, the rotation mechanism part 200 of the clutch apparatus by 2nd Embodiment is demonstrated.

  The rotation mechanism unit 200 according to the second embodiment includes a motor 201, a worm wheel 92, a spur gear 93, and a connecting member 94. The motor 201 is configured to be rotatable only in one direction. The rotation mechanism portion 200 is not provided with stoppers 95a and 95b (see FIGS. 6 and 7). The other structure of the rotation mechanism unit 200 is the same as that of the rotation mechanism unit 90.

  Then, as shown in FIG. 8, when the motor 201 is rotated in one direction from the state where the locking member 61 is discharged from the groove 56, the worm wheel 92 is rotated clockwise in FIG. At this time, the spur gear 92b is rotated together with the worm wheel 92, and the spur gear 93 meshing with the spur gear 92b is rotated counterclockwise in FIG. Thereby, the connecting member 94 is moved so as to approach the axial center of the driven-side rotator 5, and the pin 69 of the locking member 61 is inserted into the groove 56.

  When the pin 69 of the locking member 61 is inserted into the annular groove 58, energization to the motor 201 is stopped. At this time, since it is difficult to drive the worm 91 a from the worm wheel 92 side, the pin 69 of the locking member 61 is maintained in a state of being inserted into the annular groove 58.

  Thereafter, as shown in FIG. 9, when the motor 201 is rotated in one direction, the worm wheel 92 is rotated clockwise in FIG. At this time, the spur gear 92b is rotated together with the worm wheel 92, and the spur gear 93 meshing with the spur gear 92b is rotated counterclockwise in FIG. As a result, the connecting member 94 is moved away from the axis of the driven-side rotator 5, and the pin 69 of the locking member 61 is pulled out (discharged) from the annular groove 58.

  Then, when the pin 69 of the locking member 61 is discharged from the annular groove 58, the energization to the motor 201 is stopped. At this time, since it is difficult to drive the worm 91 a from the worm wheel 92 side, the pin 69 of the locking member 61 is maintained in a state of being discharged from the groove 56.

  Note that the insertion and ejection of the locking member 61 into the groove 56 may be determined based on, for example, the number of steps of the motor 201, or a sensor (not shown) that detects the position of the locking member 61 may be used. The determination may be made based on the detection result of the sensor. Further, a sensor (not shown) for detecting the position (angle) of the worm wheel 92 or the spur gear 93 may be provided, and the determination may be made based on the detection result of the sensor.

  As described above, the rotation mechanism unit 200 is provided with the motor 201 that rotates only in one direction. Each time the worm wheel 92 is rotated by the motor 201, the locking member 61 is inserted and discharged. It is comprised so that.

(effect)
In the second embodiment, as described above, by providing the motor 201 that is rotated only in one direction, there is no need to switch the energization direction to the motor 201, so that the control circuit that controls the motor 201 is simplified. Can do. In addition, in the worm 91a, the worm wheel 92, and the like, only one side of the tooth surface can be slid.

  The remaining effects of the second embodiment are similar to those of the first embodiment.

-Other embodiments-
In addition, embodiment disclosed this time is an illustration in all the points, Comprising: It does not become a basis of limited interpretation. Therefore, the technical scope of the present invention is not interpreted only by the above-described embodiments, but is defined based on the description of the scope of claims. Further, the technical scope of the present invention includes all modifications within the meaning and scope equivalent to the scope of the claims.

  For example, in the first and second embodiments, the example has been shown in which the groove depth in the formation range t2 of the side surface 57aII of the inclined groove 57 is uniform in the circumferential direction. At t2, it is good also as a structure which becomes gradually deeper from the said start end part 57c to the termination | terminus part 57d.

  Further, in the first and second embodiments, the example in which the depth of the annular groove 58 is made constant over the entire periphery is shown, but the present invention is not limited to this, and the groove depth of the start end portion 58c in the annular groove 58 is not limited to this. It may be shallower than the groove depth of other portions.

  In the first and second embodiments, the example in which the groove 56 into which the pin 69 of the locking member 61 is inserted is provided on the outer peripheral surface of the driven-side rotating body 5 is not limited to this, but the groove 56 is driven. It is good also as a structure which is provided in the inner peripheral surface of the side rotary body 5, and is inserted in the groove | channel 56 by the pin 69 of the latching member 61 inserted in the internal space of the driven side rotary body 5 moving to an outer peripheral side.

  In the first and second embodiments, the number of 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 configuration of the clutch device 1 is not limited to the ball lock type. For example, a crimp type clutch device may be used.

  Furthermore, in the first and second 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 used in a clutch device that switches the connected state of both of them by moving the driven-side rotator forward and backward relative to the drive-side rotator.

DESCRIPTION OF SYMBOLS 1 Clutch apparatus 4 Drive side rotary body 5 Driven side rotary body 57 Inclination groove 61 Locking member 90 Turning mechanism part 91 Motor 91a Worm (decelerator)
92 Worm wheel (decelerator)
94 Connecting member 200 Rotating mechanism 201 Motor

Claims (1)

A driving side rotating body;
A driven-side rotator which is provided so as to be movable between a connection position connected to the drive-side rotator and a release position where the connection is released, and in which an inclined groove is formed;
A biasing member that biases the driven-side rotating body toward the coupling position;
A locking member that can be inserted into the inclined groove of the driven-side rotating body;
A rotation mechanism for rotating the locking member,
When the locking member is inserted into the inclined groove of the driven-side rotating body by the rotation mechanism portion in a state where the driven-side rotating body is in the coupling position, the inclined groove contacts the locking member. A clutch device in which the driven-side rotator moves toward the release position along with the rotation, by contacting with the clutch device;
The rotation mechanism unit includes a motor, a reduction device that amplifies the output torque of the motor, and a connecting member that is connected to the locking member, and the output torque of the motor is amplified by the reduction device and the A clutch device configured to rotate the locking member by being transmitted to a connecting member.

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