JP2007232184A - Two-way clutch unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To relieve surface tension by a lubricant applied to a dog engagement part of a dog clutch. <P>SOLUTION: This two-way clutch unit comprises an input outer ring rotated and driven by a driving source, an output shaft 2 taking out torque transmitted from the input outer ring to the external, a clutch ring 3 disposed between the input outer ring and the output shaft 2 axially movably and relatively unrotatably, and capable of being engaged with and disengaged from the output shaft 2, and a cam mechanism controlling the engagement/disengagement of the clutch ring 3 and the output shaft 2 by axially moving the clutch ring 3. The dog clutch 24 is formed between opposed faces of the clutch ring 3 and the output shaft 2, and surface tension reducing means composed of recessed portions 25-28 are formed on the clutch ring 3 of the dog clutch 24 and the output shaft 2. <P>COPYRIGHT: (C)2007,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).

  The two-way clutch unit is interposed between an input outer ring that is rotationally driven by a drive source, an output shaft that extracts rotational torque transmitted from the input outer ring to the outside, and the input outer ring and the output shaft. And a cam mechanism that controls engagement / disengagement between the clutch ring and the output shaft by moving the clutch ring in the axial direction.

This cam mechanism is composed of a fixed cam pressed against a stationary member by an elastic member such as a spring, and a movable cam that moves the clutch ring in the axial direction by axially fitting with the fixed cam. Further, a dog clutch is formed between the opposing surfaces of the clutch ring and the output shaft, and the clutch ring and the output shaft are engaged by meshing the dogs in the dog clutch. In this dog clutch, since the dogs are repeatedly engaged with each other, lubricating oil such as grease is applied to improve durability.
JP 2005-172141 A

  Incidentally, in the two-way clutch unit disclosed in Patent Document 1 described above, lubricating oil such as grease is applied to the meshing portion of the dog clutch formed between the clutch ring and the output shaft. On the other hand, when the clutch ring and the output shaft are engaged, the dogs of the clutch ring and the output shaft are brought into close contact with each other by meshing of the dogs.

  When the dogs are in close contact with each other in this way, when the clutch ring and the output shaft are separated from each other when the input outer ring and the output shaft are disconnected in the two-way clutch unit, the dog clutches mesh with each other. A large surface tension is generated by the lubricating oil applied to the portion. As a result, it is difficult to smoothly separate the input outer ring and the output shaft, and reliability and responsiveness in the two-way clutch unit may be reduced.

  Therefore, the present invention has been proposed in view of the above-mentioned problems, and the object of the present invention is to provide a two-way clutch unit that can relieve the surface tension due to the lubricating oil applied to the meshing portion of the dog clutch. It is to provide.

  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 And a cam mechanism 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. A dog clutch is formed between the opposite surfaces of the first and second surfaces, and surface tension reducing means is provided on the dog clutch.

  In the present invention, when a dog clutch is formed between the opposing surfaces of the torque transmission member and the output system rotating member, and the surface tension reducing means is provided on the dog clutch, the torque transmission member and the output system rotating member are engaged. The degree of close contact between the dogs of the torque transmission member and the output system rotating member by the meshing of the dogs in the dog clutch is reduced.

  That is, by the surface tension reducing means described above, the contact area between the dogs in the dog clutch is reduced to reduce the surface tension of the lubricating oil. As a result, when torque is interrupted between the input system rotating member and the output system rotating member, the torque transmitting member and the output system rotating member can be easily separated to smoothly separate the input system rotating member and the output system rotating member. Can do.

  As the surface tension reducing means in the configuration described above, it is desirable to use a concave portion or a convex portion provided on one facing surface of either the torque transmitting member or the output system rotating member. With this concave or convex portion, the contact area between the torque transmission member and the output system rotating member can be reduced when the dogs in the dog clutch are engaged with each other, and the contact area can be reduced with a simple structure. it can. When the surface tension reducing means is a recess, the recess functions as a lubricating oil reservoir, so that durability can be improved.

  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, a dog clutch is formed between the opposing surfaces of the torque transmission member and the output system rotation member, and surface tension reducing means is provided on the dog clutch, so that when the torque transmission member and the output shaft are engaged, The contact area between the dogs in the dog clutch can be reduced to reduce the surface tension of the lubricating oil.

  As a result, when the torque is interrupted between the input system rotating member and the output system rotating member, the torque transmission member and the output shaft can be easily separated, and the input system rotating member and the output system rotating member can be smoothly separated. . As a result, the reliability and responsiveness in the two-way clutch unit can be improved.

  The clutch unit of the embodiment shown in FIGS. 1 and 2 includes an input outer ring 1 that is an input system rotating member that is rotationally driven by a drive source such as a motor, and an output for extracting torque transmitted from the input outer ring 1 to the outside. A clutch ring 3 which is a torque transmission member which is interposed between the output shaft 2 which is a system rotation member, the input outer ring 1 and the output shaft 2 and which can be engaged with and disengaged from the output shaft 2, and the clutch ring 3 The main part is composed of a cam mechanism 4 that controls engagement / disengagement with the output shaft 2.

  Each component consisting of the input outer ring 1, the output shaft 2, the clutch ring 3 and the cam mechanism 4 is housed in a housing 7 which is a stationary member, and the housing 7 housing each component is attached via an intermediate side plate 6. It is integrated by attaching to the side plate 5. When this clutch unit is incorporated in an electric slide door device, the input outer ring 1 is connected to a drive motor as a drive source, the output shaft 2 is connected to a slide mechanism for opening and closing the slide door, and the mounting side plate 5 is bolted. It attaches to the fixed site | part of an electric slide door apparatus by the above.

  The input outer ring 1 has a generally hollow cylindrical shape, and a worm wheel 8 is formed on the outer periphery thereof. The worm wheel 8 meshes with a worm (not shown) that is rotationally driven by a drive motor (not shown) to constitute a worm gear. A notch-shaped window hole 9 is formed in a part of the housing 7 in the circumferential direction, and the worm wheel 8 and the worm mesh with each other in the window hole 9. In addition, as a power transmission mechanism between a drive source such as a drive motor and the input outer ring 1, it is possible to employ a winding transmission device or the like in addition to the gear illustrated in the drawings.

  The output shaft 2 includes a large-diameter portion fitted in the input outer ring 1, an intermediate-diameter portion fitted in the end of the housing 7, and a small-diameter portion protruding from the housing 7 and connected to the slide mechanism described above. The outer ring 1 and the housing 7 are rotatably supported. As shown in FIG. 3B, a dog 10 projects from an end face 2a of the output shaft 2 facing the clutch ring 3 having a large diameter portion. In this embodiment, the case where four dogs 10 are arranged on the output shaft 2 at equal intervals in the circumferential direction is illustrated, but the number of dogs 10 is arbitrary.

  On the other hand, the clutch ring 3 is slidable in the axial direction with respect to the input outer ring 1 and mounted so as not to be relatively rotatable. That is, as shown in FIG. 5A, the inner diameter of the outer ring 1 is formed with the grooves 11 along the axial direction at equal intervals in the circumferential direction. The protrusions 12 that fit into the concave grooves 11 are formed at equal intervals in the circumferential direction along the axial direction. A dog 13 projects from an end surface 3a of the clutch ring 3 facing the output shaft 2 as shown in FIG. 3A, and a dog clutch 24 is formed by the dog 10 of the output shaft 2 described above. . In this embodiment, the case where four dogs 13 are arranged on the clutch ring 3 at equal intervals in the circumferential direction is illustrated. However, the number of the dogs 13 is arbitrary, and the dogs of the output shaft 2 are arranged. It is sufficient to match the number of ten.

  When the clutch ring 3 moves along the axial direction to the side closer to the output shaft 2 and the dog 13 of the clutch ring 3 meshes with the dog 10 of the output shaft 2, they are integrated in the rotational direction and torque is transmitted. . Further, when the clutch ring 3 moves away from the output shaft 2 along the axial direction from the meshing state of both, and the dog 13 of the clutch ring 3 is detached from the dog 10 of the output shaft 2, the two are separated. Torque is cut off.

  In the dog clutch 24 composed of the dog 10 of the output shaft 2 and the dog 13 of the clutch ring 3, when the clutch ring 3 and the output shaft 2 are to be detached, the lubricating oil applied to the meshing portions of the dogs 10, 13 is used. Surface tension is generated. For this reason, the dog clutch 24 is provided with surface tension reducing means for relaxing the surface tension caused by the lubricating oil.

  As the surface tension reducing means, a concave portion is provided on the surface of the output shaft 2 facing the clutch ring 3 as shown in FIGS. That is, the recess 25 is provided on the front end surface of the dog 10 of the output shaft 2 and the recess 26 is provided on the surface 2 a facing the clutch ring 3. A recess is provided on the surface of the clutch ring 3 facing the output shaft 2. That is, the concave portion 27 is provided on the front end surface of the dog 13 of the clutch ring 3 and the concave portion 28 is provided on the surface 3 a facing the output shaft 2. When the surface tension reducing means is the recesses 25 to 28, the recesses 25 to 28 also function as a lubricating oil reservoir, and durability can be improved.

  As other surface tension reducing means, as shown in FIGS. 4 (a) and 4 (b), a convex portion 29 is provided on the front end surface of the dog 10 of the output shaft 2, and the front end surface of the dog 13 of the clutch ring 3 is convex. The part 30 may be provided. In this embodiment, concave portions 25 to 28 (see FIGS. 3A and 3B) or convex portions 29 and 30 [see FIGS. 4A and 4B] are provided on both the output shaft 2 and the clutch ring 3. Although provided, a concave portion or a convex portion may be provided on either the output shaft 2 or the clutch ring 3.

  By providing such surface tension reducing means, it is possible to reduce the contact area between the clutch ring 3 and the output shaft 2 when the dogs 10 and 13 of the dog clutch 24 are engaged with each other. A reduction in contact area can be realized. By reducing the contact area, the surface tension of the lubricating oil can be relaxed, and when the torque between the input outer ring 1 and the output shaft 2 is interrupted, the clutch ring 3 and the output shaft 2 can be easily separated from each other. And the output shaft 2 can be smoothly separated, and reliability and responsiveness can be improved.

  A compression coil spring 14 (hereinafter simply referred to as a first spring) is interposed between the output shaft 2 and the clutch ring 3 and presses them in directions away from each other. The elastic force of the first spring 14 prevents the clutch ring 3 and the output shaft 2 from meshing when the drive motor is stopped. The biasing force that causes the clutch ring 3 and the output shaft 2 to be separated by the first spring 14 is stopped by a retaining ring 15 that is mounted at a substantially central portion in the axial direction of the inner diameter of the input outer ring 1. The amount of movement away from is regulated.

  The cam mechanism 4 disposed on the opposite side of the output shaft 2 across the clutch ring 3 is composed of a fixed cam 16 and a movable cam 17. A compression coil spring 18 (hereinafter simply referred to as a second spring) is provided between the movable cam 17 and the clutch ring 3 to bias the elastic force in the direction in which they are separated from each other. ing. Further, the above-described three members, that is, the output shaft 2, the clutch ring 3, and the movable cam 17, are coaxially disposed so as to be slidable on a support shaft 19 fitted in the center thereof.

  The movable cam 17 is slidable in the axial direction with respect to the input outer ring 1 and is mounted so as not to be relatively rotatable. That is, as shown in FIG. 5B, the outer diameter of the movable cam 17 is set to correspond to the above-described concave groove 11 formed along the axial direction at equal intervals in the circumferential direction on the inner diameter of the input outer ring 1. The protrusions 20 that fit into the concave grooves 11 are formed at equal intervals in the circumferential direction along the axial direction. The end surface of the movable cam 17 facing the fixed cam 16 is composed of an inclined surface 21a and a flat surface 21b projecting from the end surface as shown in FIGS. 6 (a), 6 (b) and 8, and is fixed. A cam surface 21 that can be fitted to the cam 16 in the axial direction is formed.

  On the other hand, the fixed cam 16 has a flange at its axial end, and a wave spring 22 that is an elastic member is interposed between the flange and the inner diameter end of the intermediate side plate 6. (See FIG. 1). Due to the elastic force of the wave spring 22, the fixed cam 16 is pressed against the stationary attachment side plate 5 so that a frictional resistance is generated between the end surface of the fixed cam 16 and the attachment side plate 5. The end surface of the fixed cam 16 facing the movable cam 17 is composed of an inclined surface 23a and a flat surface 23b recessed from the end surface as shown in FIGS. 7 (a), 7 (b) and 8, and is movable. A cam surface 23 that can be fitted to the cam 17 in the axial direction is formed.

  When the inclined surface 21a of the movable cam 17 and the inclined surface 23a of the fixed cam 16 are fitted in the axial direction, the movable cam 17 moves toward the side closer to the clutch ring 3 along the axial direction with respect to the fixed cam 16. To do. Due to the axial movement of the clutch ring 3, an elastic force is accumulated in the second spring 18 between the movable cam 17 and the clutch ring 3, and when the elastic force of the first spring 14 between the clutch ring 3 and the output shaft 2 is overcome, The clutch ring 3 moves along the axial direction toward the side close to the output shaft 2. Due to the axial movement of the clutch ring 3, the dog 13 of the clutch ring 3 and the dog 10 of the output shaft 2 are engaged with each other.

  An operation example of the 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 16 and the movable cam 17 are in a neutral state in which the flat surfaces 23b and 21b are in contact with each other (see FIG. 8). 18 is in contact with the fixed cam 16 by the elastic force. The clutch ring 3 is urged in a direction away from the output shaft 2 by the elastic force of the first spring 14, and is disengaged from the dog 10 of the output shaft 2 by a retaining ring 15 disposed on the inner diameter of the housing 7. It is regulated. Since the dog 13 of the clutch ring 3 and the dog 10 of the output shaft 2 are not engaged with each other in this way, the output shaft 2 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 1 starts to rotate through the worm gear, and the rotational force of the drive motor is transmitted to the input outer ring 1 at a reduced speed by the worm gear. Since the movable cam 17 is regulated in the rotational direction by being concavo-convexly fitted to the input outer ring 1 by the concave grooves 11 and the protrusions 20, the movable cam 17 rotates with the input outer ring 1. On the other hand, since the fixed cam 16 is fixed in the rotational direction, the above-described movable cam 17 rotates along the cam surface 21 fitted with the fixed cam 16, that is, the inclined surface 21a. It moves to the output shaft side along the axial direction by rotation. As the movable cam 17 moves in the axial direction, the second spring 18 between the movable cam 17 and the clutch ring 3 is compressed in the axial direction, and the elastic force is accumulated. When the compression force overcomes the elastic force of the first spring 14 between the clutch ring 3 and the output shaft 2, the clutch ring 3 moves in the axial direction and approaches the output shaft 2 (see FIG. 9).

  Similarly to the movable cam 17, the clutch ring 3 is also rotated in accordance with the input outer ring 1 because it is regulated in the rotational direction by engaging the input outer ring 1 with concave and convex grooves 11 and protrusions 12. . Therefore, the clutch ring 3 meshes with the output shaft 2 when the meshing phase between the dog 13 of the clutch ring 3 and the dog 10 of the output shaft 2 matches due to the rotation and axial movement of the clutch ring 3. Thereby, the rotational torque of the input outer ring | wheel 1 is transmitted to the output shaft 2 via the clutch ring 3, and a door can be opened and closed electrically.

  At this time, as described above, the movable cam 17 rotates along with the input outer ring 1 and the fixed cam 16 receives the rotational force from the movable cam 17 and rotates in the same direction. In order to receive the frictional resistance due to the pressing, the axial force is transmitted to the movable cam 17 by the frictional resistance. Note that a lubricant such as grease is appropriately sealed in a frictional sliding portion including between the fixed cam 16 and the attachment side plate 5.

  When the dog 13 of the clutch ring 3 and the dog 10 of the output shaft 2 are in the same phase during the rotation of the drive motor, the dogs are in contact with each other and the clutch ring 3 and the output shaft 2 are not fitted. However, since the output shaft 2 is not rotationally driven, the output shaft 2 does not rotate because a load is applied to the output shaft 2. However, if the drive motor continues to rotate as it is, the rotational phase of the input outer ring 1 and the movable cam 17 advances with respect to the output shaft 2, so that the meshing phase of the dog 13 of the clutch ring 3 and the dog 10 of the output shaft 2 matches. By the way, the clutch ring 3 is instantaneously moved in the axial direction by the elastic force of the second spring 18 in which the elastic force is accumulated, and the clutch ring 3 and the output shaft 2 are engaged with each other.

  Next, when the drive motor is stopped from its rotating state, the clutch ring 3 and the output shaft 2 are in mesh with each other. In this state, since the output shaft 2 cannot be rotated in a free state, the drive motor may be rotated in the direction opposite to the rotation direction of the drive motor described above. That is, in a state where the clutch ring 3 and the output shaft 2 are engaged with each other, the inclined surfaces 21a and 23a of the movable cam 17 and the fixed cam 16 are joined together as shown by the broken line in FIG. The fixed cam 16 is separated from the flat surface 23b. When the drive motor is reversed from this state, the flat surface 21b of the movable cam 17 can be shifted to a state where the flat surface 23b of the fixed cam 16 is in contact (see the solid line in FIG. 10).

  The reversal angle of the drive motor at this time is based on the phase of the movable cam 17 with respect to the fixed cam 16 when the flat surface 21b of the movable cam 17 is separated from the fixed cam 16, as shown by the solid line in FIG. Since the rotation angle α up to the phase at which the flat surface 21b comes into contact with the fixed cam 16 is sufficient, the reverse angle of the drive motor can be set in advance. When the drive motor is reversed, the flat surface 23b of the fixed cam 16 with which the flat surface 21b of the movable cam 17 contacts is larger than the circumferential dimension of the flat surface 21b of the movable cam 17 to provide a backlash β. Therefore, the reversal operation of the input outer ring 1 can be allowed, and the output shaft 2 is not driven to be reversed.

  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 2 of the clutch unit rotates freely unless the drive motor is rotated, so that it can be easily opened and closed manually without dragging the drive motor. . Further, if a potentiometer is attached to the output shaft 2, the position of the door can be sensed even in a half-door state, and if it is switched to the electric mode, it can be opened and closed by a drive motor.

  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. (A) is a perspective view which shows the clutch ring of embodiment of FIG. 1, (b) is a perspective view which shows the output shaft of embodiment of FIG. (A) is a perspective view which shows the clutch ring of other embodiment, (b) is a perspective view which shows the output shaft of other embodiment. (A) is sectional drawing which follows the AA line of FIG. 1, (b) is sectional drawing which follows the BB line of FIG. (A) is a left view which shows the movable cam which comprises the cam mechanism of FIG. 1, (b) is sectional drawing which follows the CC line of (a). (A) is a right view which shows the fixed cam which comprises the cam mechanism 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. 6 and the fixed cam of FIG. 7 fitted. It is sectional drawing for demonstrating operation | movement of each component of a clutch unit. It is sectional drawing for demonstrating the fitting state of the movable cam with respect to a fixed cam.

Explanation of symbols

1 Input system rotating member (input outer ring)
2 Output system rotating member (output shaft)
3 Torque transmission member (clutch ring)
4 Cam mechanism 7 Static system member (housing)
10, 13 Dog 24 Dog clutch 25-28 Concave part 29, 30 Convex part

Claims (4)

  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 cam mechanism for controlling engagement / disengagement between the torque transmission member and the output system rotation member, and a dog clutch is formed between the opposing surfaces of the torque transmission member and the output system rotation member. A two-way clutch unit comprising a tension reducing means.   2. The two-way clutch unit according to claim 1, wherein the surface tension reducing means is a recess provided on at least one of the opposing surfaces of the torque transmission member and the output system rotating member in the dog clutch.   2. The two-way clutch unit according to claim 1, wherein the surface tension reducing means is a convex portion provided on at least one of the opposing surfaces of the torque transmission member or the output system rotation member in the dog clutch.   4. The apparatus according to claim 1, wherein the input system rotating member is connected to a drive motor, and the output system rotating member is connected to a door slide mechanism, so that the input system rotating member is incorporated in the electric slide door device. Way clutch unit.

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