JP2007309426A - Two-way clutch unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce the number of parts and product cost, and to improve assemblability while reducing weight with resin component parts. <P>SOLUTION: The two-way clutch unit is provided with: static system members 25 to 27; an input outer ring 21 rotation-driven by a drive source; an output shaft 22 for taking out torque transmitted from the input outer ring 21 to outside; a clutch ring 23, provided between the input outer ring 21 and the output shaft 22 in such a manner as to move in an axial direction and incapable of relative rotation, and to engage and to disengage with the output shaft 22; and a cam mechanism 24 for controlling engagement and disengagement of the clutch ring 23 and the output shaft 22 by moving the clutch ring 23 in the axial direction via a relative angle displacement for the static system members 25 to 27. A projection 39 for restricting movement of the clutch ring 23 in the axial direction is integrally provided for the clutch ring 23. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention is used for opening / closing mechanisms such as an electric slide door, an electric back door, an electric curtain, an electric shutter, etc. in a power window of an automobile, a one-box car, and the like. The present invention relates to a two-way clutch unit that transmits and interrupts transmission of torque when a drive source is stopped to enable manual operation of an output system.

  For example, there is an electric slide door device of an automobile (one box car) in which a drive motor and a door are connected or disconnected by a two-way clutch unit. The two-way clutch unit incorporates a dog clutch that connects and disconnects input and output by a cam mechanism (see, for example, Patent Document 1). FIG. 12 shows a schematic configuration of the 2-way clutch unit disclosed in Patent Document 1.

  The two-way clutch unit is interposed between an input outer ring 1 that is rotationally driven by a drive motor, an output shaft 2 that extracts the rotational torque transmitted from the input outer ring 1 to the outside, and the input outer ring 1 and the output shaft 2. A clutch ring 3 that can be engaged / disengaged with the output shaft 2, and a cam mechanism 4 that controls engagement / disengagement between the clutch ring 3 and the output shaft 2 by moving the clutch ring 3 in the axial direction; It consists of the main parts consisting of

  This cam mechanism 4 is movable to move the clutch ring 3 in the axial direction via the coil spring 12 by fitting the stationary cam 5 pressed against the stationary member 5 by the wave spring 6 with the fixed cam 7 in the axial direction. It consists of a cam 8.

  Further, a dog clutch 9 is formed on the clutch ring 3 and the output shaft 2, and the clutch ring 3 and the output shaft are engaged by the engagement of the dogs 10, 11 in the dog clutch 9 by the axial movement of the clutch ring 3 to the right in the figure. 2 is engaged.

  On the other hand, a coil spring 13 is interposed between the clutch ring 3 and the output shaft 2, and an elastic force is urged so as to separate them from each other. Due to the elastic force of the coil spring 13, when the drive motor is stopped, the clutch ring 3 is pressed to the left in the figure and is separated from the output shaft 2. Therefore, the dog clutch 9 of the clutch ring 3 and the output shaft 2 The dogs 10 and 11 are not engaged with each other.

In order to restrict the axial movement of the clutch ring 3 to the left in the figure, a retaining ring 14 is attached to the inner diameter of the input outer ring 1, and the clutch ring 3 is locked to the retaining ring 14 when the clutch ring 3 moves in the axial direction. I try to let them.
JP 2005-172141 A

  By the way, since the 2-way clutch unit disclosed in Patent Document 1 described above is suitable for an electric slide door device, it is required to reduce its weight because it is stored inside the door. In response to this demand for weight reduction, it is preferable to adopt a resin that is lightweight and can be manufactured at low cost as a component constituting the two-way clutch unit.

  On the other hand, in the conventional two-way clutch unit, a coil spring that applies an urging force that separates the clutch ring 3 and the output shaft 2 in order to prevent the clutch ring 3 and the output shaft 2 from meshing when the drive motor is stopped. 13 has a structure in which the clutch ring 3 is interposed between the clutch ring 3 and the output shaft 2, and a retaining ring 14 for restricting the amount of axial movement of the clutch ring 3 away from the output shaft 2 is required. .

  As shown in FIG. 13, the retaining ring 14 is mounted by being fitted into a slit groove 15 provided along the circumferential direction on the inner diameter of the input outer ring 1. Here, the input outer ring 1 is made of resin, whereas the retaining ring 14 is usually made of a metal material such as iron. Therefore, when the metal retaining ring 14 is fitted into the slit groove 15 of the resin input outer ring 1, the retaining ring 14 may damage the input outer ring 1, and the input outer ring 1 is damaged due to the scratch. May cause.

  In addition, forming the retaining ring slit groove 15 in the inner diameter of the resin input outer ring 1 requires complicated processing, resulting in an increase in the cost of the product. Further, since the retaining ring 14 is required as a component, the number of parts is increased, and a complicated assembly work for fitting the retaining ring 14 into the slit groove 15 of the input outer ring 1 is also required.

  Therefore, the present invention has been proposed in view of the above-mentioned problems, and its object is to reduce the number of parts and product cost and to improve assembly while achieving weight reduction with resin components. Is to provide a two-way clutch unit capable of achieving the above.

  As technical means for achieving the aforementioned object, the present invention provides a stationary system member, an input system rotation member that is rotationally driven by a drive source, and a torque transmitted from the input system rotation member. An output system rotating member, a torque transmitting member that is axially movable between the input system rotating member and the output system rotating member and that cannot be relatively rotated, and that can be engaged with and disengaged from the output system rotating member, and stationary A control member for controlling engagement / disengagement between the torque transmission member and the output system rotation member by moving the torque transmission member in the axial direction through relative angular displacement with respect to the system member, and The regulating means for regulating is provided integrally with the torque transmission member.

  In the present invention, a restricting means for restricting the axial movement of the torque transmitting member is provided integrally with the torque transmitting member. That is, as a restricting means for restricting the axial movement of the torque transmission member, conventionally, a retaining ring which is one component has been used. However, in the present invention, the retaining member is integrated with the torque transmission member without using the retaining ring. The function provided by the retaining ring, that is, the axial movement of the torque transmission member, is regulated by the restricting means provided for the purpose. As a result, it is not necessary to assemble a retaining ring which is a separate part, and the assembly of the retaining ring does not damage the counterpart part, so that the assemblability can be improved and the number of parts and the product cost can be reduced.

  Note that the restricting means in the present invention is preferably constituted by a protrusion extending in the axial direction from the torque transmitting member and capable of contacting the control member. As described above, by causing the protrusion extending in the axial direction from the torque transmitting member to contact the control member, the axial movement of the torque transmitting member can be restricted. Since this protrusion is formed integrally with the torque transmission member, it is not necessary to assemble it to the counterpart part, so that the assemblability can be improved and the number of parts and the product cost can be reduced.

  The two-way clutch unit of the present invention can be applied by being incorporated in an electric slide door device by connecting an input system rotating member to a drive motor and connecting an output system rotating member to a door slide mechanism. . In this case, by controlling the engagement / disengagement between the torque transmission member and the output system rotation member, when the drive motor and the slide door are connected, an electric opening / closing operation is possible, and when the drive motor and the slide door are not connected, Manual opening and closing operations are possible.

  According to the present invention, since the restricting means for restricting the axial movement of the torque transmitting member is integrally provided in the torque transmitting member, a retaining ring as a separate part that has been used conventionally is not required, and the retaining ring is assembled. This will not damage the mating parts, improve assembly, reduce the number of parts and product cost, simplify the structure, and make it easier to reduce the weight of the 2-way clutch unit. . As a result, it is possible to provide an optimal two-way clutch unit when applied to an electric sliding door device.

  Hereinafter, an embodiment in which the two-way clutch unit according to the present invention is applied to, for example, an electric sliding door device of an automobile (one box car) will be described in detail.

  The clutch unit of the embodiment shown in FIG. 1 and FIG. 2 is for taking out an input outer ring 21 as an input system rotating member that is rotationally driven by a drive motor as a drive source, and a torque transmitted from the input outer ring 21 to the outside. An output shaft 22 that is an output system rotating member, a clutch ring 23 that is interposed between the input outer ring 21 and the output shaft 22, and is capable of engaging and disengaging with the output shaft 22, and the clutch ring 23 And a cam mechanism 24 as a control member for controlling engagement / disengagement between the output shaft 22 and the output shaft 22.

  Each component including the input outer ring 21, the output shaft 22, the clutch ring 23, and the cam mechanism 24 is accommodated in a housing 25, and the housing 25 accommodating each component is mounted on the attachment side plate 27 via the intermediate side plate 26. Are integrated. The housing 25, the intermediate side plate 26, and the mounting side plate 27 constitute a stationary system member.

  When this clutch unit is incorporated in an electric slide door device, the input outer ring 21 is connected to a drive motor as a drive source, the output shaft 22 is connected to a slide mechanism that opens and closes the slide door, and the mounting side plate 27 is bolted. It attaches to the fixed site | part of an electric slide door apparatus by the above.

  The input outer ring 21 has a generally hollow cylindrical shape, and a worm wheel 28 is formed on the outer periphery thereof. The worm wheel 28 meshes with a worm (not shown) that is rotationally driven by a drive motor (not shown) to form a worm gear. A notch-shaped window hole 29 is formed in a part of the housing 25 in the circumferential direction, and the worm wheel 28 and the worm mesh with each other in the window hole 29. In addition, as a power transmission mechanism between a drive source such as a drive motor and the input outer ring 21, it is possible to employ a winding transmission device in addition to the gear illustrated in the drawings.

  The output shaft 22 includes a large-diameter portion fitted in the input outer ring 21, an intermediate-diameter portion fitted in the end portion of the housing 25, and a small-diameter portion protruding from the housing 25 and connected to the above-described slide mechanism. The outer ring 21 and the housing 25 are rotatably supported. As shown in FIG. 3, a dog 30 protrudes in the axial direction on the end face of the output shaft 22 facing the large-diameter clutch ring 23. In this embodiment, the case where four dogs 30 are arranged on the output shaft 22 at equal intervals in the circumferential direction is illustrated, but the number of dogs 30 is arbitrary.

  On the other hand, the clutch ring 23 is slidable in the axial direction with respect to the input outer ring 21 and is mounted so as not to be relatively rotatable. That is, as shown in FIGS. 5 and 6, the inner diameter of the input outer ring 21 is formed with the groove 31 along the axial direction at equal intervals in the circumferential direction, and the outer diameter of the clutch ring 23 corresponding to this is formed. As shown in FIG. 4 and FIG. 6, convex portions 32 that fit into the concave grooves 31 protrude outward in the radial direction at equal intervals in the circumferential direction. The clutch ring 23 is slidable in the axial direction in a state in which the clutch ring 23 cannot be rotated relative to the input outer ring 21 by fitting the convex portion 32 into the concave groove 31. That is, the clutch ring 23 rotates together with the input outer ring 21.

  As shown in FIG. 4, a dog 33 projects in the axial direction on the end surface of the clutch ring 23 facing the output shaft 22, and a dog clutch 34 is formed with the dog 30 of the output shaft 22 described above. The In this embodiment, the case where four dogs 33 are arranged on the clutch ring 23 at equal intervals in the circumferential direction is illustrated, but the number of the dogs 33 is arbitrary and the dogs 30 of the output shaft 22 are arbitrary. It is sufficient to match the number of.

  When the clutch ring 23 moves along the axial direction to the side closer to the output shaft 22 and the dog 33 of the clutch ring 23 meshes with the dog 30 of the output shaft 22, they are integrated in the rotational direction and torque is transmitted. . Further, when the clutch ring 23 moves away from the output shaft 22 along the axial direction from the meshed state of both, and the dog 33 of the clutch ring 23 is detached from the dog 30 of the output shaft 22, the two are separated. Torque is cut off.

  The output shaft 22 and the clutch ring 23 are arranged coaxially by inserting a support shaft 36 planted in the central concave hole 35 of the output shaft 22 into the central through hole 37 of the clutch ring 23, and On the other hand, the clutch ring 23 is movable in the axial direction. Further, a coil spring 38 is interposed between the output shaft 22 and the clutch ring 23, and an elastic force is urged in a direction to separate them from each other. The elastic force of the coil spring 38 prevents the clutch ring 23 and the output shaft 22 from meshing when the drive motor is stopped.

  As shown in FIG. 1 and FIG. 4, the clutch ring 23 has a protrusion 32 that protrudes radially outward and extends in the axial direction toward the opposite side of the output shaft 22 to form a protrusion 39. . The tip of the projection 39 can come into contact with the fixed cam 40 of the cam mechanism 24, and the biasing force that separates the clutch ring 23 and the output shaft 22 by the coil spring 38 described above is applied to the projection 39 of the clutch ring 23. The tip is stopped by contacting the fixed cam 40, and the amount of movement of the clutch ring 23 away from the output shaft 22 is restricted.

  As described above, the retaining ring 14 (see FIG. 12), which is one component, has been conventionally used as the restricting means for restricting the axial movement of the clutch ring 23. In this embodiment, this retaining ring is used. Instead, the protrusion 39 integrally provided on the clutch ring 23 is configured to abut the tip of the protrusion 39 against the fixed cam 40 when the clutch ring 23 moves in the axial direction. As a result, it is not necessary to assemble a retaining ring which is a separate part, and the assembly of the retaining ring does not damage the counterpart part, so that the assemblability can be improved and the number of parts and the product cost can be reduced.

  The cam mechanism 24 disposed on the opposite side of the output shaft 22 with the clutch ring 23 interposed therebetween is composed of a fixed cam 40 and a movable cam 41. A coil spring 42 is provided between the movable cam 41 and the above-described clutch ring 23 to bias the elastic force in a direction in which they are separated from each other. Similarly to the clutch ring 23, the support shaft 36 planted in the central concave hole 35 of the output shaft 22 is coaxially disposed by being inserted into the central through hole 43 of the movable cam 41, and is fixed to the fixed cam 40. The movable cam 41 is movable in the axial direction.

  The movable cam 41 is slidable in the axial direction with respect to the input outer ring 21 and is mounted so as not to be relatively rotatable. That is, as shown in FIGS. 5 and 7, the outer diameter of the movable cam 41 corresponds to the concave grooves 44 formed along the axial direction at equal intervals in the circumferential direction on the inner diameter of the input outer ring 21. Protrusions 45 that fit into the grooves 44 are formed at equal intervals in the circumferential direction. As a result, the movable cam 41 rotates together with the input outer ring 21. The end surface of the movable cam 41 facing the fixed cam 40 is composed of an inclined surface 46a and a flat surface 46b projecting from the end surface as shown in FIGS. 8 (a), 8 (b) and 10, and is fixed. A cam surface 46 that can be fitted in the cam 40 in the axial direction is formed.

  On the other hand, the fixed cam 40 has a flange portion at its axial end portion, and a wave spring 47 that is an elastic member is interposed between the flange portion and the inner diameter end portion of the intermediate side plate 26. (See FIG. 1). Due to the elastic force of the wave spring 47, the fixed cam 40 is pressed against the stationary attachment side plate 27, and a frictional resistance is generated between the end surface of the fixed cam 40 and the attachment side plate 27. The end surface of the fixed cam 40 facing the movable cam 41 is composed of an inclined surface 48a and a flat surface 48b which are recessed from the end surface as shown in FIGS. 9 (a), 9 (b) and 10, and is movable. A cam surface 48 that can be fitted to the cam 41 in the axial direction is formed.

  An operation example of the two-way clutch unit of the embodiment having the above-described configuration will be described in detail below.

  When the drive motor is stopped, the fixed cam 40 and the movable cam 41 are in a neutral state in which the flat surfaces 48b and 46b are in contact with each other (see FIGS. 10 and 11A). 41 is in a state of contacting the fixed cam 40 by the elastic force of the coil spring 42. Further, the clutch ring 23 is urged in a direction away from the output shaft 22 by the elastic force of the coil spring 38, and the clutch ring 23 is separated from the dog 30 of the output shaft 22 while the protrusion 39 is in contact with the fixed cam 40. It is regulated. Since the dog 33 of the clutch ring 23 and the dog 30 of the output shaft 22 are not engaged with each other in this manner, the output shaft 22 is free to rotate from the output shaft side, and the door is manually operated. Can be opened and closed freely.

  On the other hand, when the drive motor rotates, the input outer ring 21 starts to rotate through the worm gear, and the rotational force of the drive motor is transmitted to the input outer ring 21 at a reduced speed by the worm gear. Since the movable cam 41 is regulated in the rotational direction by fitting the concave portion 44 and the convex portion 45 to the input outer ring 21 in a concave and convex manner, the movable cam 41 rotates with the input outer ring 21. On the other hand, since the fixed cam 40 is fixed in the rotational direction, the aforementioned movable cam 41 rotates along the cam surface 46 fitted to the fixed cam 40, that is, the inclined surface 46a. It moves to the output shaft side along the axial direction by rotation [see FIG. 11 (b)]. By the movement of the movable cam 41 in the axial direction, the coil spring 42 between the movable cam 41 and the clutch ring 23 is compressed in the axial direction, and the elastic force is accumulated. When the compression force overcomes the elastic force of the coil spring 38 between the clutch ring 23 and the output shaft 22, the clutch ring 23 moves in the axial direction and approaches the output shaft 22.

  Similarly to the movable cam 41, the clutch ring 23 is also restricted in the rotational direction by engaging the input outer ring 21 with the concave groove 31 and the convex portion 32, so that it rotates with the input outer ring 21. . Therefore, the clutch ring 23 meshes with the output shaft 22 when the meshing phase of the dog 33 of the clutch ring 23 and the dog 30 of the output shaft 22 match due to the rotation and axial movement of the clutch ring 23. Thereby, the rotational torque of the input outer ring | wheel 21 is transmitted to the output shaft 22 via the clutch ring 23, and can open and close a door electrically.

  At this time, as described above, the movable cam 41 rotates with the input outer ring 21, and the fixed cam 40 receives the rotational force from the movable cam 41 and rotates the same, but the wave spring 47 from the mounting side plate 27 which is a stationary system. In order to receive the frictional resistance due to the pressing, the axial force is transmitted to the movable cam 41 by the frictional resistance. Note that a lubricant such as grease is appropriately sealed in the frictional sliding portion including between the fixed cam 40 and the attachment side plate 27.

  In addition, when the dog 33 of the clutch ring 23 and the dog 30 of the output shaft 22 are in the same phase during the rotation of the drive motor, the dogs are in contact with each other and the clutch ring 23 and the output shaft 22 are not fitted. However, since the output shaft 22 is not rotationally driven, the output shaft 22 does not rotate because a load is applied to the output shaft 22. However, if the drive motor continues to rotate as it is, the rotational phase of the input outer ring 21 and the movable cam 41 advances with respect to the output shaft 22, so that the meshing phase of the dog 33 of the clutch ring 23 and the dog 30 of the output shaft 22 matches. By the way, the clutch ring 23 is instantaneously moved in the axial direction by the elastic force of the coil spring 42 in which the elastic force is accumulated, and the clutch ring 23 and the output shaft 22 are engaged with each other.

  By installing the clutch unit as described above in the door drive part of the electric slide door of the automobile, when the electric mode is selected by the switch in the car, the clutch unit is rotated by the rotation of the drive motor when the door is driven electrically. The door can be opened and closed via the door, and if the door knob is opened by hand, the door can be opened and closed by driving the motor by sensing it.

  On the other hand, if the manual mode is selected by the switch in the vehicle, the output shaft 22 of the clutch unit rotates freely unless the drive motor is rotated. Therefore, it can be easily opened and closed manually without dragging the drive motor. . Further, if a potentiometer is attached to the output shaft 22, the position of the door can be sensed even in a half-door state, and can be opened and closed by a drive motor by switching to the electric mode.

  In the above-described embodiment, the case where the clutch unit is incorporated in the electric sliding door device in the one-box car has been described, but the present invention is an apparatus that drives a load from a drive motor via a speed reducer, for example, a power window of an automobile, The present invention can be applied to an apparatus having a specification for switching between electric and manual in an open / close mechanism such as an electric back door, an electric curtain, and an electric shutter.

It is sectional drawing which shows embodiment of the 2 way clutch unit which concerns on this invention. It is a right view of FIG. It is a perspective view which shows the output shaft of embodiment of FIG. It is a perspective view which shows the clutch ring of embodiment of FIG. It is a perspective view which shows the input outer ring | wheel of embodiment of FIG. It is sectional drawing which follows the AA line of FIG. It is sectional drawing which follows the BB line of FIG. (A) is a right view which shows the movable cam of FIG. 1, (b) is sectional drawing which follows the CC line of (a). (A) is a right view which shows the fixed cam of FIG. 1, (b) is sectional drawing which follows the DD line | wire of (a). It is sectional drawing which shows the state which the movable cam of FIG.8 (b) and the fixed cam of FIG.9 (b) fitted. FIG. 8B shows a state in which the movable cam and the fixed cam shown in FIG. 9B are fitted, where FIG. 8A shows a state before starting the drive motor, and FIG. 8B shows a partially enlarged state after the drive motor starts. It is sectional drawing. It is sectional drawing which shows the prior art example of a 2 way clutch unit. It is a perspective view which shows the input outer ring | wheel in the 2-way clutch unit of FIG.

Explanation of symbols

21 Input system rotating member (input outer ring)
22 Output system rotating member (output shaft)
23 Torque transmission member (clutch ring)
24 Control member (cam mechanism)
25, 26, 27 Stationary system member 39 Control means (protrusion)

Claims (3)

  A stationary system member, an input system rotational member that is rotationally driven by a drive source, an output system rotational member that extracts torque transmitted from the input system rotational member, and an input system rotational member and an output system rotational member. The torque transmitting member is moved in the axial direction through a relative angular displacement with respect to the stationary system member, and a torque transmitting member that is movable in the axial direction and is relatively non-rotatable. And a control member for controlling engagement / disengagement between the torque transmission member and the output system rotation member, and a restriction means for restricting axial movement of the torque transmission member is provided integrally with the torque transmission member. 2-way clutch unit.   2. The two-way clutch unit according to claim 1, wherein the restricting unit includes a protrusion extending in an axial direction from the torque transmission member and capable of contacting the control member.   3. The two-way clutch unit according to claim 1, wherein the two-way clutch unit is incorporated in the electric slide door device by connecting the input system rotating member to a drive motor and connecting the output system rotating member to a door slide mechanism.

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