JP2005163852A - Clutch mechanism of power plant - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a power plant with a clutch mechanism capable of continuously maintaining the engaged state of a clutch even if a solenoid coil is deenergized. <P>SOLUTION: This clutch mechanism of the power plant comprises a motor 24, a wire drum 30 moving a slide door 11 in a door closing direction and a door opening direction, and a clutch mechanism 31 installed between the motor 24 and the wire drum 30 and having a solenoid coil part 60. The clutch mechanism 31 comprises a normal clutch engagement state for transmitting the rotation of the motor 24 to the wire drum 30, a clutch disengagement state for making the wire drum 30 and the motor 24 in a non-connection state to each other, and a brake clutch engagement state for maintaining the connection of the wire drum 30 to the motor 24 even in the off state of the solenoid coil part 60 and preventing it from returning to the clutch disengagement state unless the solenoid coil part 60 is turned on. A normal clutch connection power release control to reversely rotate the motor 24 by continuously turning on the solenoid coil part 60 and then turning on the solenoid coil part 60 and the motor 24 is installed in a control part 88 controlling the motor 24 and the solenoid coil part 60. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a clutch mechanism of a power unit, and more particularly to a clutch mechanism that can transmit a large torque with a small electromagnetic coil portion, and can maintain a clutch connected state even when the electromagnetic coil is turned off. The present invention relates to a clutch mechanism. As an example of the power device in which the clutch mechanism of the present invention is used, a power slide device that slides the vehicle slide door in the door opening direction and the door closing direction can be cited.

Conventional vehicle sliding doors include a power sliding device that slides the sliding door in the opening and closing directions with motor power, a power closing device that moves the sliding door in the half latch position to the full latch position with motor power, and motor power. A power device such as a power release device for unlatching the door latch device of the sliding door is provided.
The power device, particularly a power device used as a power slide device, is provided with a clutch mechanism that transmits the power of the motor to the slide door. Clutch mechanisms are roughly classified into mechanical clutch mechanisms and electromagnetic clutch mechanisms, each having advantages and disadvantages.
The merit of the mechanical clutch mechanism is that it can be manufactured at a low cost with few electrical components. However, there is a disadvantage that a time lag occurs in connecting and disconnecting the clutch, and the control system becomes complicated due to this time lag.

In contrast, the electromagnetic clutch mechanism has the advantages of simple control and instant connection and disconnection, but the electromagnetic clutch mechanism that can be applied to a high output power device such as a power slide device has its electromagnetic coil. It has the disadvantage that the part becomes large and expensive.
The reason why the electromagnetic coil part is enlarged will be described. There are also types of electromagnetic clutch mechanisms, which can be classified into friction type and meshing type. In the friction type clutch, the clutch is connected by bringing the armature into contact with the friction rotating plate by the magnetic force of the electromagnetic coil portion, and the size of the output that can be transmitted depends on the size of the friction coefficient between the armature and the friction rotating plate. . For this reason, a high-power power device such as a power slide device requires a strong electromagnetic coil section so that a large friction coefficient can be obtained.

On the other hand, in the meshing clutch, the clutch is connected by meshing the concave and convex meshing portion of the armature with the rotating plate similarly formed in the concave and convex shape by the magnetic force of the electromagnetic coil portion. In this way, if it is uneven engagement, the transmission output is not affected by the engagement force, but in the engagement type, the movement distance of the armature is remarkably increased. The distance that the frictional armature is attracted by the magnetic force of the electromagnetic coil is as short as 1 mm or less. However, in the case of the meshing armature, the moving distance becomes as long as 3 to 5 mm. Therefore, the electromagnetic coil portion that can move the meshing armature is also inevitably increased in size.
In order to solve the above problem, the present applicant has proposed a power unit including a rational clutch mechanism in which a mechanical clutch mechanism and an electromagnetic clutch mechanism are fused (Patent Document 1).
Japanese Patent Application No. 2002-194014

In the invention of the prior application, since the clutch is disengaged when the electromagnetic coil portion is turned off, there are problems in operability and convenience.
Therefore, the present invention provides a clutch mechanism of a power unit that can continue the clutch engagement state even when the electromagnetic coil portion is turned off, and provides a method for releasing the clutch engagement state in this clutch mechanism.

  Therefore, the present invention relates to the wheel 26 that rotates around the support shaft 28 by the power of the motor 24, the fixed gear body 69 supported by the support shaft 28, and the fixed gear body 69 when moved to the normal clutch coupling position. The movable gear body 65 is disengaged from the fixed gear body 69 when the gear 26 is engaged and the rotation of the wheel 26 can be transmitted to the fixed gear body 69 and moved to the clutch disengaged position, and the movable gear body 65 is brought to the clutch disengaged position. In the clutch mechanism 31 including the clutch release spring 70 that biases the motor 24, the moving gear body 65 moves through either the clutch coupling direction or the clutch disengagement direction through the wheel 26. It is engaged with the wheel 26 so as to receive a rotational force, and the clutch mechanism 31 is further relative to the moving gear body 65. When the armature 61 is turned, the armature 61 that can displace the movable gear body 65 to the clutch coupling position against the elasticity of the clutch release spring 70 and the armature 61 are attracted by a magnetic force to give a brake resistance to the armature 61. An electromagnetic coil portion 60 capable of restricting the co-rotation state of the armature 61 and the moving gear body 65, and when the motor 24 and the electromagnetic coil portion 60 are both turned on, the moving gear body 65 is in the normal clutch engagement position. The clutch mechanism 31 is in a normal clutch connection state in which the rotation of the motor 24 is transmitted to the fixed gear body 69, and the armature 61 is moved from the normal clutch connection position to the armature 61 by the elasticity of the clutch release spring 70. Engagement with the fixed gear body 69 on the way back in the cutting direction The moving gear body 65 is brought into contact with the moving gear body 65 before being disengaged, and the clutch mechanism 31 is held by holding the moving gear body 65 at a brake clutch connecting position where the engagement of the moving gear body 65 and the fixed gear body 69 is continued. A clutch holding surface 64D that can be engaged with a brake clutch is provided, and the armature 61 is in contact with the clutch holding surface 64D and the moving gear body 65 when the moving gear body 65 rotates when the electromagnetic coil portion 60 is off. The control unit 88 that controls the motor 24 and the electromagnetic coil unit 60 continues to turn on the electromagnetic coil unit 60 so that the moving gear body 65 and the armature 61 are in a co-rotating state. The motor 24 is rotated in the reverse direction in a state where the movement is regulated to release the contact between the moving gear body 65 and the clutch holding surface 64D. This is a clutch mechanism of a power unit provided with a normal clutch coupling power release control for turning off the electromagnetic coil unit 60 and the motor 24.

  According to the clutch mechanism of the present invention, the clutch engagement state can be continued even when the electromagnetic coil unit 60 is turned off. For this reason, for example, when the power device of the present invention is used in a power slide device, the slide door 11 serving as a driven member can be held in a state of being connected to the speed reduction mechanism of the motor 24. It becomes possible to hold the door in a desired position. This clutch engagement state can be released under the control of the control unit.

  An embodiment of the present invention will be described with reference to the drawings. Reference numeral 10 denotes a vehicle body, and 11 a slide door slidably attached to the vehicle body 10, and slides between a closed position and an open position that close the door opening 12 of the vehicle body 10. Moving. In the present invention, the opening position of the sliding door 11 is the position where the sliding door 11 is fully opened (hereinafter referred to as a complete opening position, but usually has a width of several centimeters), the closing position and the opening position. A distinction is made between two types of intermediate opening positions (see FIG. 1).

  An upper rail 13 is fixed to the vehicle body 10 near the upper portion of the door opening 12, a lower rail 14 is fixed to the vehicle body 10 near the lower portion of the door opening 12, and a center rail 16 is attached to the quarter panel 15 on the rear side surface of the vehicle body 10. Is fixed. The slide door 11 includes an upper bracket 17 slidably engaged with the upper rail 13, a lower bracket 18 slidably engaged with the lower rail 14, and a center bracket 19 slidably engaged with the center rail 16. Provided. The brackets 17, 18, and 19 are preferably pivotally fixed to the slide door 11, and the slide door 11 is slidable in the opening direction and the closing direction by engagement of these brackets and rails.

  A power unit 20 having motor power is provided in the internal space 50 (FIG. 2) of the slide door 11. As shown in FIGS. 6 and 7, the power unit 20 is provided with a wire drum 30 for pulling and pulling the wire cable. The wire drum 30 has two wire cables, that is, a door opening cable 21 ′ and a door closing. When the wire drum 30 rotates in the opening direction, the opening cable 21 ′ is wound up and the closing cable 21 ″ is pulled out, and the wire drum 30 is moved in the closing direction. When rotated, the door opening cable 21 'is drawn out and the door closing cable 21 "is wound up.

  As shown in FIG. 4, the opening cable 21 ′ is directed from the lower position on the front side of the slide door 11, that is, the position near the lower bracket 18, toward the vehicle body side (lower bracket 18 side) outside the slide door 11. Pulled out. The lower bracket 18 is provided with a pulley 22 having a vertical axis, and a door opening cable 21 ′ drawn out from the slide door 11 passes through the front side of the pulley 22 and then extends rearward in the lower rail 14 to the rear of the lower rail 14. It is fixed to the vehicle body 10 at or near the end. Accordingly, when the opening cable 21 ′ is wound in the closed state, the sliding door 11 slides backward (in the opening direction) via the lower bracket 18.

  As shown in FIG. 5, the closing cable 21 ″ is connected to the vehicle body side (center bracket 19 side) from the upper and lower central portions on the rear side of the sliding door 11, that is, from the position near the center bracket 19 to the outside of the sliding door 11. The center bracket 19 is provided with a pulley 23 having a vertical axis, and the closing cable 21 ″ drawn from the slide door 11 passes through the rear side of the pulley 23 and then passes through the center rail 16. It extends forward and is fixed to the vehicle body 10 at or near the front end of the center rail 16. Thus, when the door closing cable 21 ″ is wound in the open state, the slide door 11 slides forward (in the door closing direction) via the center bracket 19.

  FIG. 8 shows a tension mechanism 100 that maintains the tension of the wire cable 30 at an appropriate pressure, and is preferably provided in the power unit 20. A pair of tension rollers 102 and 103 with which the cables 21 ′ and 21 ″ abut are provided in the case 101 of the tension mechanism 100. The tension rollers 102 and 103 are fixed by tension shafts 104 and 105, and the tension spring 106 A tension sensor 107 is urged to approach each other with elasticity, and detects the amount of movement of the tension rollers 102 and 103.

  6 and 7, a cylindrical worm 25 is attached to the output shaft of the high-power motor 24, and a first worm wheel 26 and a second worm wheel 27 are cylindrical on both sides of the axial center of the cylindrical worm 25, respectively. It is provided so as to mesh with the worm 25. The first worm wheel 26 is fixed in the case 29 of the power unit 20 by a first support shaft 28, and the wire drum 30 is also fixed to the first support shaft 28. A first clutch mechanism 31, which will be described in detail later, is provided between the first worm wheel 26 and the wire drum 30, and when the first clutch mechanism 31 is turned on, the rotation of the first worm wheel 26 is applied to the wire drum 30. When transmitted and turned off, the wire drum 30 becomes free with respect to the first worm wheel 26. Therefore, in FIG. 6, when the first clutch mechanism 31 is turned on while the first worm wheel 26 is rotating clockwise by the normal rotation of the motor 24, the wire drum 30 is also rotated clockwise to open the door opening cable 21. When the first clutch mechanism 31 is turned on while the first worm wheel 26 is rotating counterclockwise due to the reverse rotation of the motor 24, the wire drum 30 is also turned on. By rotating counterclockwise, the door opening cable 21 'is wound up and the door closing cable 21 "is pulled out. The function of rotating the wire drum 30 by the power of the motor 24 to wind and pull out the cables 21 ′ and 21 ″ is the power slide function (device) of the power unit 20.

  In the relationship between the cylindrical worm 25 and the first worm wheel 26, the cylindrical worm 25 is not practically rotated by the rotational force applied to the first worm wheel 26. It is desirable that the cylindrical worm 25 can be rotated by applying a fairly strong force to the first worm wheel 26.

  The second worm wheel 27 is fixed in the case 29 of the power unit 20 by the second support shaft 32. One end of the second support shaft 32 penetrates the case 29 and protrudes outward, and the swing arm 33 is fixed to the protruding end. A second clutch mechanism 34 is provided between the second worm wheel 27 and the second support shaft 32, and when the second clutch mechanism 34 is turned on, the rotation of the second worm wheel 27 is oscillated through the second support shaft 32. When transmitted to the moving arm 33 and turned off, the swinging arm 33 becomes free with respect to the second worm wheel 27.

  One end of a release cable 35 is engaged with the pivot end of the swing arm 33. The other end of the release cable 35 is connected to the door latch unit 36 (FIGS. 1 and 9) of the slide door 11, and when the release cable 35 is pulled in the direction of arrow A by the swing of the swing arm 33, the door latch unit 36 is configured to be released. An example of the door latch unit 36 is shown in FIG. 9, and the door latch unit 36 includes a latch 38 that engages with a striker 37 fixed to the vehicle body 10, and a ratchet 39 that engages with the latch 38. Is urged in the clockwise direction by the elasticity of the latch spring 40, and the ratchet 39 is urged in the counterclockwise direction by the elasticity of the ratchet spring 41. When the sliding door 11 moves in the closing direction, the latch 38 comes into contact with the striker 37, and the ratchet 39 engages with the half latch step 42 of the latch 38 from the open position (unlatched position) indicated by the solid line. Through this position, the ratchet 39 rotates to a full latch position (a position indicated by a dotted line) where the ratchet 39 engages with the full latch step 43 of the latch 38. When the latch 38 reaches the full latch position, the slide door 11 is completely closed. The release cable 35 is connected to a ratchet 39. When the release cable 35 is pulled in the direction of arrow A, the ratchet 39 is released from the latch 38, the door latch unit 36 is unlatched, and the slide door 11 can be opened. It becomes a state. The function of swinging the swing arm 33 by the power of the motor 24 and unlatching the door latch unit 36 is the power release function of the power unit 20.

  The first clutch mechanism 31 shown in FIG. 7 is a clutch having an electromagnetic coil part 60 that is turned on / off by electric control. In general, when the electromagnetic coil part 60 is turned on, the first clutch mechanism 31 is in a connected state. Thus, when it is turned off, it is in a disconnected state. However, as will be described later, it has a feature that it can maintain the clutch engaged state (brake clutch connected state) even when the electromagnetic coil unit 60 is turned off. The electromagnetic coil part 60 has a cylindrical shape arranged around the first support shaft 28, the electromagnetic coil part 60 is fixed to the case 29, and the first support shaft 28 is rotatable with respect to the electromagnetic coil part 60. ing. The first worm wheel 26 is rotatably supported on the outer periphery of the electromagnetic coil unit 60. In FIG. 7, an annular armature 61 is disposed close to the left of the electromagnetic coil section 60, and the armature 61 is rotatably supported by the first support shaft 28 and is movable in the axial direction. The armature 61 is urged to the left so as to be separated from the electromagnetic coil portion 60 by the weak elasticity of the brake release spring 62 and is in contact with the step portion of the first support shaft 28. When the electromagnetic coil unit 60 is turned on, the right surface of the armature 61 is attracted by the magnetic force of the electromagnetic coil unit 60 against the elasticity of the brake release spring 62 and closely contacts the left surface of the electromagnetic coil unit 60. The frictional resistance generated by this close contact becomes a brake resistance necessary for clutch engagement. First, since the necessary brake resistance is small, and second, the armature 61 can be disposed close to the electromagnetic coil unit 60. The generated magnetic force of the electromagnetic coil unit 60 may be weak, and thus a lightweight, small and inexpensive electromagnetic coil unit can be used.

  A cam body 63 is fixed to the left surface of the armature 61. The armature 61 and the cam body 63 move integrally, and may be integrally formed. As shown in FIG. 10, the cam surface 64 of the cam body 63 includes a top portion 64 </ b> A that swells to the left in the axial direction of the first support shaft 28, a bottom portion 64 </ b> B formed by a notch, and a slope 64 </ b> C that connects them. It is an annular concavo-convex surface. The slope 64C is a two-stage slope having a clutch holding surface 64D in the middle, and the middle clutch holding surface 64D has a function of maintaining the first clutch mechanism 31 in the brake clutch engaged state when the electromagnetic coil unit 60 is off. . FIG. 12 shows the detailed shape of the cam surface 64, the inclined surface 64C is preferably an inclined surface of about 30 degrees with respect to the axis X of the first support shaft 28, and the clutch holding surface 64D is connected to the axis X. Although it may be a flat surface orthogonal to the surface, it is preferably formed on a receding surface of about 10 degrees.

  In FIG. 7, a moving gear body 65 (FIG. 11) is provided on the left side of the cam body 63. The moving gear body 65 is rotatably supported by the first support shaft 28 and is axially movable, and a plurality of leg portions 66 extending toward the first worm wheel 26 on the right side are provided on the outer periphery thereof. Is formed. As shown in FIGS. 7 and 13, the right end of the leg 66 is engaged with the engagement groove 67 of the first worm wheel 26, and the moving gear body 65 is also interlocked with the rotation of the first worm wheel 26. It is designed to rotate. The leg portion 66 is slidable in the axial direction of the first support shaft 28 with respect to the engagement groove 67, but even if the moving gear body 65 moves to the left at the maximum, the leg portion 66 and the engagement groove 67 Therefore, the movable gear body 65 and the first worm wheel 26 always rotate integrally. Further, as shown in FIG. 14, a gap Y in the rotational direction is formed between the leg 66 and the engagement groove 67, and the leg 66 (moving gear body 65) is engaged with the engagement groove 67 (first worm wheel). 26) is set so that it can freely rotate by about 6 degrees. On the left surface of the moving gear body 65, a moving annular gear portion 68 centered on the first support shaft 28 is provided.

  A fixed gear body 69 is disposed on the left side of the moving gear body 65, and a clutch release spring 70 that presses the moving gear body 65 to the right is provided between the moving gear body 65 and the fixed gear body 69. . The left surface of the fixed gear body 69 is fixed to the wire drum 30, and both rotate integrally. The wire drum 30 is fixed to the left end of the first support shaft 28 so as to rotate integrally with the first support shaft 28. A fixed annular gear portion 71 is provided on the right surface of the fixed gear body 69. When the movable gear body 65 slides to the left with respect to the first support shaft 28 against the elasticity of the clutch release spring 70, the movable annular gear portion. 68 meshes with the fixed annular gear portion 71. The state in which the gear portion 68 and the gear portion 71 mesh with each other is the normal clutch engagement state of the first clutch mechanism 31, and the rotation of the first worm wheel 26 is transmitted to the wire drum 30. On the other hand, when the moving gear body 65 slides to the right with respect to the first support shaft 28 by the elasticity of the clutch release spring 70, the moving annular gear portion 68 is disengaged from the fixed annular gear portion 71 and the clutch is disengaged. The rotation of the 1 worm wheel 26 is not transmitted to the wire drum 30.

  The moving gear body 65 is formed with a cam surface 72 that slides the moving gear body 65 to the left against the elasticity of the clutch release spring 70 in cooperation with the cam surface 64 of the cam body 63. As shown in FIG. 11, the cam surface 72 is a regular annular uneven surface having a top portion 72 </ b> A that swells rightward in the axial direction of the first support shaft 28, a bottom portion 72 </ b> B, and a slope 72 </ b> C that connects them. . The cam surface 72 has a substantially symmetrical structure with respect to the cam surface 64, but in this embodiment, no clutch holding surface is provided. However, if the clutch holding surface is formed on either one of the cam surface 64 and the cam surface 72, the desired effect is obtained. As shown in FIG. 15, the inclined surface 72C of the cam surface 72 is replaced with the clutch holding surface 72D. It may be a two-step slope provided.

  When the moving gear body 65 is slid rightward by the elasticity of the clutch release spring 70, the top portion 72A of the cam surface 72 is normally aligned with the bottom portion 64B of the cam surface 64 as shown in FIGS. The part 68 is detached from the fixed annular gear part 71 and is in a clutch disengaged state. In this clutch disengaged state, when the electromagnetic coil unit 60 is turned on, the right surface of the armature 61 resists the elasticity of the brake release spring 62 and is attracted to the left surface (friction surface) of the electromagnetic coil unit 60 by a magnetic force. In addition, a brake resistance is applied to the cam body 63. Next, when the moving gear body 65 (cam surface 72) is rotated by the power of the motor 24, the cam body 63 is in a state in which the rotation is restricted by the brake resistance. The cam surface 72 and the cam surface 64 of the cam body 63 are out of phase, and the moving gear body 65 is pushed to the left against the elasticity of the clutch release spring 70, and the moving annular gear portion 68 is pushed as shown in FIG. Meshes with the fixed annular gear portion 71 and is normally engaged with the clutch.

  When both the motor 24 and the electromagnetic coil unit 60 are turned off in the normal clutch engagement state of FIGS. 19 and 20, the armature 61 and the cam body 63 are released from the brake resistance. Then, the moving gear body 65 moves to the right while rotating the cam body 63 in the escape direction (downward in FIG. 19) due to the elasticity of the clutch release spring 70, and the moving gear body 65 meshes with the fixed gear body 69. Before the state is removed, as shown in FIGS. 21 and 22, the top portion 72 </ b> A of the moving gear body 65 comes into contact with the clutch holding surface 64 </ b> D of the cam body 63, whereby the moving gear body 65 can rotate the cam body 63. It will not be possible, and movement to the right will be restricted. For this reason, even if the electromagnetic coil part 60 is an OFF state, the meshing with the moving gear body 65 and the fixed gear body 69 is maintained, and the 1st clutch mechanism 31 will be in a brake clutch connection state.

  21 and 22, the moving gear body 65, the armature 61, and the cam body 63 are maintained in a state of rotating integrally by resistance due to contact between the top portion 72A and the clutch holding surface 64D. . Therefore, even if the fixed gear body 69 is rotated upward in order to move the moving gear body 65 upward in FIG. 22, the armature 61 and the cam body 63 also move up in conjunction with each other. Is not released. Note that the frictional force between the top 72A and the clutch holding surface 64D required to keep the moving gear body 65 and the cam body 63 in an integrated state is such that the clutch holding surface 64D acts on the axis X of the first support shaft 28. Even a flat surface orthogonal to the surface can be secured, but good friction can be obtained when the clutch holding surface 64D is set to a receding surface of about 10 degrees.

  The abutment between the top portion 72A and the clutch holding surface 64D is achieved by turning on the electromagnetic coil portion 60 after the electromagnetic coil portion 60 is turned on, as will be described later. It can be released by moving upward in FIGS. The rotation angle of the moving gear body 65 required at this time is about 5 degrees, and the free rotation angle of the moving gear body 65 obtained by the gap Y formed between the leg 66 and the engagement groove 67 ( Is set smaller than about 6 degrees).

  The second clutch mechanism 34 has substantially the same structure as the first clutch mechanism 31, 73 is a cylindrical electromagnetic coil portion, 74 is an annular armature, 75 is a brake release spring, 76 is a cam body, and 77 is a cam body. 76 cam surface, 78 is a moving gear body, 79 is a leg portion, 80 is an engaging groove, 81 is an annular moving gear portion, 82 is a fixed gear body, 83 is a clutch release spring, 84 is a fixed annular gear portion, 85 is This is a cam surface of the moving gear body 78. The fixed gear body 82 of the second clutch mechanism 34 is fixed to a receiving member 86 fixed to the left end of the second support shaft 32. The second clutch mechanism 34 does not have a brake clutch connected state.

  In FIG. 9, 44 is a power close device attached to the inside of the slide door 11, and the motor power of the power close device 44 is transmitted to the latch 38 of the door latch unit 36 via the close cable 45. In the illustrated embodiment, the power closing device 44 is a separate device from the power unit 20. The power closing device 44 pulls the closing cable 45 to rotate the latch 38 from the half latch position to the full latch position when the latch 38 is in the half latch position due to the movement of the slide door 11 in the closing direction. Close the door completely.

  In FIG. 7, one end of the first support shaft 28 penetrates the case 29 and protrudes outward. A gear 51 is fixed to the protruding end, and a rotating body 52 is engaged with the gear 51. . When the first support shaft 28 is rotated by the rotation of the wire drum 30, the rotating body 52 rotates in conjunction with the rotation. Reference numeral 53 denotes a control board of the power unit 20, and a drum rotation sensor 54 that directly detects the rotation (and the rotation direction and rotation speed) of the rotating body 52 (wire drum 30) is directly attached to the control board 53. A preferred embodiment of the rotator 52 and the sensor 54 include an S pole magnetic body and an N pole magnetic body arranged at intervals in the circumferential direction, and the sensor 54 is a hole for detecting magnetism. IC. If the sensor 54 is directly attached to the control board 53, a harness is not required, which is advantageous against external electric noise.

  In FIG. 1, reference numeral 87 denotes an opening handle of the sliding door 11, and the opening handle 87 is connected to the ratchet 39 of the door latch unit 36 to release the ratchet 39 from the latch 38.

  In FIG. 16, 88 is a control unit, 89 is a handle switch for detecting the opening operation of the door opening handle 89, and 90 is a rotation detection sensor for detecting the rotation of the motor 24. To detect.

  The power unit 20 shown in FIGS. 6 and 7 has a power slide function and a power release function, and is configured to share a single motor 24 for both functions.

(Function)
The operation of the first clutch mechanism 31 will be described. In a state where the electromagnetic coil unit 60 is off, no substantial frictional resistance is generated between the armature 61 and the electromagnetic coil unit 60. In this state, when the cylindrical worm 25 is rotated by forward rotation of the motor 24, the first worm wheel 26 rotates clockwise in FIG. 6, and the moving gear body 65 is also engaged by the engagement between the leg 66 and the engagement groove 67. Rotate the clock. At this time, the moving gear body 65 is moved to the right by the elasticity of the clutch release spring 70, and the moving gear portion 68 of the moving gear body 65 is fixed to the fixed gear portion 71 of the fixed gear body 69 as shown in FIGS. The cam surface 72 of the moving gear body 65 is in contact with the cam surface 64 of the cam body 63 so as to be close to each other as shown in FIG. Therefore, when the motor 24 is rotated forward in this state, the moving gear body 65, the cam body 63, and the armature 61 integrated with the cam body 63 rotate together, and the moving gear body 65 becomes the fixed gear body 69. Do not move towards. .

  When the electromagnetic coil unit 60 is turned on in the above state (FIGS. 17 and 18), the armature 61 is attracted to the electromagnetic coil unit 60 by the generated magnetic force against the elasticity of the brake release spring 62, and the electromagnetic coil unit 60 and the armature 61. A predetermined brake resistance is generated between the armature 61 and the cam body 63, thereby restricting the rotation of the armature 61 and the cam body 63. The moving gear body 65 is relative to the cam body 63 about the first support shaft 28. Rotate to. Then, the cam surface 72 and the cam surface 64 are out of phase as shown in FIG. 19, and the moving gear body 65 is pushed out toward the fixed gear body 69 against the elasticity of the clutch release spring 70, as shown in FIG. In addition, the moving annular gear portion 68 of the moving gear body 65 is engaged with the fixed gear portion 71 of the fixed gear body 69 to be in the normal clutch engaged state. As a result, the rotation of the motor 24 is transmitted to the wire drum 30 via the fixed gear body 69, the door closing cable 21 "is wound up, and the slide door 11 moves in the door closing direction. The armature 61 and the cam body 63 also rotate with the moving gear body 65.

  When the motor 24 and the electromagnetic coil unit 60 are turned off while the sliding door 11 is moving in the closing direction, the moving gear body 65 engaged with the first worm wheel 26 stops rotating, and the armature 61 and The cam body 63 is released from the brake resistance, and the moving gear body 65 is returned to the right while rotating the cam body 63 in the escape direction (downward in FIGS. 19 and 20) by the elasticity of the clutch release spring 70. Then, before the moving gear body 65 is disengaged from the fixed gear body 69, the top portion 72A of the moving gear body 65 contacts the clutch holding surface 64D of the cam body 63, as shown in FIGS. As a result, the moving gear body 65 cannot rotate the cam body 63 and the rightward movement is also restricted. For this reason, even if the electromagnetic coil unit 60 is in an off state, the brake clutch connected state in which the moving gear body 65 meshes with the fixed gear body 69 is maintained. In such a brake clutch connected state, the slide door 11 is directly connected to the speed reduction mechanism on the motor 24 side, and thus is substantially kept stationary. Therefore, if the user intentionally turns off the motor 24 and the electromagnetic coil unit 60, the slide door 11 can be held at a desired intermediate opening position. In addition, when this halfway stop is performed by automatic control by the control unit 88, it is possible to easily stop and hold the state where the slide door 11 is opened about half by automatic operation.

  When the sliding door 11 is moved to the closing position by the normal closing control by the control unit 88 (at this time, the first clutch mechanism 31 is in the normal clutch engagement state of FIGS. 19 and 20), the motor 24 is operated for a predetermined time (a predetermined amount). Only reverse. Then, since the electromagnetic coil unit 60 is kept on, the armature 61 and the cam body 63 remain, and the moving gear body 65 moves upward in FIG. 20 by a predetermined amount, and as shown in FIGS. The top 72A of the body 65 moves above the clutch holding surface 64D of the cam body 63. In this state, the electromagnetic coil unit 60 and the motor 24 are turned off. As a result, the moving gear body 65 moves to the right without the abutment 72A coming into contact with the clutch holding surface 64D of the cam body 63 due to the elasticity of the clutch release spring 70, and returns to the clutch disengaged state of FIGS.

  Next, the release of the brake clutch connected state (FIGS. 21 and 22) of the first clutch mechanism 31 will be described. To switch the brake clutch engaged state to the clutch disengaged state, first, the electromagnetic coil unit 60 is turned on. Then, the armature 61 and the cam body 63 are attracted to the electromagnetic coil part 60, and brake resistance is provided. At this stage, the moving gear body 65 is also slightly moved to the right by the elasticity of the clutch release spring 70, but the meshing with the fixed gear body 69 is continued. Next, when power is applied, the motor 24 is rotated to rotate the moving gear body 65 upward in the case of FIG. 22 so that the top 72A of the moving gear body 65 is located above the clutch holding surface 64D of the cam body 63. When moved, the electromagnetic coil unit 60 and the motor 24 are turned off. Then, the moving gear body 65 moves to the right without the abutment 72A coming into contact with the clutch holding surface 64D of the cam body 63 due to the elasticity of the clutch release spring 70, and returns to the clutch disengaged state of FIGS.

  When the brake clutch engagement state is manually released instead of the power of the motor 24, the slide door 11 is manually moved after the electromagnetic coil unit 60 is turned on. Then, the wire drum 30 rotates and the moving gear body 65 also rotates through the fixed gear body 69. At this time, in the brake clutch connected state, the wire drum 30 is connected to the motor 24 side. However, the moving gear body 65 is about to be moved by the gap Y formed between the leg 66 and the engaging groove 67. Since the first worm wheel 26 can be freely rotated about 6 degrees, the slide door 11 can be moved with a light operating force without rotating the first worm wheel 26 to rotate the moving gear body 65. Next, when the top 72A of the moving gear body 65 is disengaged from the clutch holding surface 64D of the cam body 63 due to the rotation of the moving gear body 65, the moving gear body 65 is moved to the right by the elasticity of the clutch release spring 70, and FIGS. Return to the clutch disengaged state.

  In the manual release of the brake clutch engagement state, when the control unit 88 detects a manual clutch release operation, the electromagnetic coil unit 60 is turned on for a certain period of time as brake clutch engagement manual release control. Although many clutch manual release operations can be considered, in the present invention, first, the door opening operation of the door opening handle 87 of the slide door 11 is regarded as a clutch manual release operation. Second, the clutch manual release operation may also be considered when the slide door 11 is moved by a predetermined amount by manual force. The sliding door 11 can be moved by a predetermined amount by detecting the amount of rotation of the wire drum 30. In this case, however, the sliding door 11 is lighter by the gap Y formed between the leg 66 and the engaging groove 67. It is desirable to set the movement amount beyond the distance that can be moved by operation. If the set movement amount is small, the brake clutch connection manual release control may be performed unexpectedly by leaning against the slide door 11. The movement of the slide door 11 by a predetermined amount can also be detected by the sensor 107 of the tension mechanism 100. When the slide door 11 is moved with a strong force, the tension rollers 102 and 103 are made elastic by the tension spring 106. Since it moves against this, this movement may be detected by the sensor 107. Thirdly, a predetermined number of repetitive movements of the sliding door 11 in the opening and closing directions by manual force may be regarded as a manual clutch release operation. A person unfamiliar with the operation method of the slide door 11 is expected to intuitively move the slide door 11 in the opening direction and the closing direction when facing the situation where the slide door 11 does not move in the middle. For this reason, even if the movement amount of the slide door 11 is within the movement amount that can be moved by a light operation by the gap Y formed between the leg portion 66 and the engagement groove 67, the opening direction and the closing door are repeated. When moving in the direction, the brake clutch connection manual release control is performed.

  As described above, the brake clutch connected state of the clutch mechanism 31 according to the present invention is maintained even when the electromagnetic coil unit 60 is off, and even if the brake clutch connected state is maintained for a long period of time, the power consumption by this function is substantially reduced. It becomes zero. For this reason, the utilization method which hold | maintains the sliding door 11 in a fully open position using this function is feasible. Therefore, in the present invention, when the sliding door 11 moves to the fully opened position by the normal opening control by the control unit 88 (at this time, the first clutch mechanism 31 is in the normal clutch engagement state of FIGS. 19 and 20), The motor 24 and the electromagnetic coil unit 60 are turned off. Then, the moving gear body 65 engaged with the first worm wheel 26 stops rotating, the armature 61 and the cam body 63 are released from the brake resistance, and the elastic force of the clutch release spring 70 causes the moving gear body 65 to move to the cam body. 63 is returned to the right while rotating in the escape direction (downward in FIGS. 19 and 20). Then, before the moving gear body 65 is disengaged from the fixed gear body 69, the top portion 72A of the moving gear body 65 abuts on the clutch holding surface 64D of the cam body 63 as shown in FIGS. The mechanism 31 is maintained in the brake clutch connected state. In this brake clutch connected state, a strong resistance due to the engagement between the cylindrical worm 25 and the first worm wheel 26 acts on the slide door 11 to sufficiently satisfy the holding force necessary for holding the slide door 11 and is conventionally used. The so-called “fully opened position holder” can be dispensed with. In addition, the resistance caused by the engagement between the cylindrical worm 25 and the first worm wheel 26 may be set to be weak, and the sliding door 11 may be held in the fully opened position in cooperation with the “fully opened position holder”. In this case, since the resistance caused by the engagement between the cylindrical worm 25 and the first worm wheel 26 can be set weak, it is relatively easy to manually move the slide door 11 when the power unit 20 fails.

The side view which showed the rear part side surface of the vehicle provided with the sliding door. Schematic of the closed state. Schematic of the open state. The top view of a lower bracket. The top view of a center bracket. The side view of a power unit. Sectional drawing of the said power unit. The top view of the tension mechanism of the said power unit. Sectional drawing of a door latch unit. The perspective view of a cam body. The perspective view of a moving gear body. Detailed view of the cam surface of the cam body. Sectional drawing which shows the engagement state of the engagement groove | channel of a 1st worm wheel, and the leg part of a moving gear body. 4 is a schematic diagram showing a gap between the engagement groove and the leg portion. Sectional drawing which shows the clutch holding surface of a moving gear body. Block circuit diagram. The side view which shows the cam surface of a cam body at the time of a clutch disengagement state, and the cam surface of a moving gear body. FIG. 18 is a schematic diagram illustrating a movable gear body and a fixed gear body in a clutch disengaged state corresponding to FIG. 17. The side view which shows the cam surface of the cam body at the time of a clutch connection state, and the cam surface of a moving gear body. FIG. 20 is a schematic diagram illustrating a moving gear body and a fixed gear body in a clutch engagement state corresponding to FIG. 19. The side view which shows the cam surface of the cam body of a brake clutch connection state in an OFF state and a cam surface of a moving gear body in an electromagnetic coil part. FIG. 22 is a schematic diagram showing a moving gear body and a fixed gear body in a brake clutch connected state corresponding to FIG. 21. The side view which shows the cam surface of the cam body in the middle of releasing a brake clutch connection state, and the cam surface of a moving gear body. 24 is a schematic diagram showing a moving gear body and a fixed gear body in the middle of releasing the clutch engagement state corresponding to FIG.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Vehicle body, 11 ... Sliding door, 12 ... Door opening, 13 ... Upper rail, 14 ... Lower rail, 15 ... Quarter panel, 16 ... Center rail, 17 ... Upper bracket, 18 ... Lower bracket, 19 ... Center bracket, 20 ... Power unit, 21 '... Opening cable, 21 "... Closing cable, 22 ... Pulley, 23 ... Pulley, 24 ... Motor, 25 ... Cylindrical worm, 26 ... First worm wheel, 27 ... Second worm wheel, 28 ... 1st support shaft, 29 ... Case, 30 ... Wire drum, 31 ... 1st clutch mechanism, 32 ... 2nd support shaft, 33 ... Swing arm, 34 ... 2nd clutch mechanism, 35 ... Release cable, 36 ... Door latch Unit: 37 ... striker, 38 ... latch, 39 ... ratchet, 40 ... latch spring, 41 ... ratchet Toe spring, 42 ... Half latch step, 43 ... Full latch step, 44 ... Power close device, 45 ... Close cable, 50 ... Internal space, 51 ... Gear, 52 ... Rotating body, 53 ... Control board, 54 ... Drum rotation sensor 60 ... Electromagnetic coil part, 61 ... Armature, 62 ... Brake release spring, 63 ... Cam body, 64 ... Cam surface, 64A ... Top part, 64B ... Bottom part, 64C ... Slope, 64D ... Clutch holding surface, 65 ... Moving gear body , 66 ... Leg part, 67 ... Engaging groove, 68 ... Moving annular gear part, 69 ... Fixed gear body, 70 ... Clutch release spring, 71 ... Fixed annular gear part, 72 ... Cam surface, 72A ... Top part, 72B ... Bottom part , 72C ... slope, 72D ... clutch holding surface, 73 ... electromagnetic coil section, 74 ... armature, 75 ... brake release spring, 76 ... cam body, 77 ... cam surface, 78 ... moving gear body 79 ... Leg part, 80 ... Engaging groove, 81 ... Moving annular gear part, 82 ... Fixed gear body, 83 ... Clutch release spring, 84 ... Fixed annular gear part, 85 ... Cam surface, 86 ... Receiving member, 87 ... Open Door handle, 88 ... control unit, 89 ... handle switch, 90 ... rotation detection sensor, 100 ... tension mechanism, 101 ... case, 102, 103 ... tension roller, 104, 105 ... tension shaft, 106 ... tension spring, 107 ... tension Sensor, X ... axis, Y ... gap.

Claims (3)

A wheel 26 that rotates around the support shaft 28 by the power of the motor 24, a fixed gear body 69 supported by the support shaft 28, and a normal clutch engagement position when the wheel 26 moves to the clutch coupling position, meshes with the fixed gear body 69 and the wheel 26. A rotation gear that can be transmitted to the fixed gear body 69 and disengaged from the fixed gear body 69 when moved to the clutch disengaged position, and a clutch that urges the movable gear body 65 toward the clutch disengaged position. In the clutch mechanism 31 including the release spring 70, the moving gear body 65 can receive the rotational force of the motor 24 via the wheel 26 even if it moves in either the clutch connecting direction or the clutch disengaging direction. And the clutch mechanism 31 is further rotated relative to the moving gear body 65 to engage the clutch mechanism 31. An armature 61 capable of displacing the movable gear body 65 to the clutch coupling position against the elasticity of the hose release spring 70, and applying a brake resistance to the armature 61 by attracting the armature 61 by a magnetic force, the armature 61. And an electromagnetic coil portion 60 that can regulate the co-rotation state of the movable gear body 65. When both the motor 24 and the electromagnetic coil portion 60 are turned on, the movable gear body 65 is displaced to the normal clutch coupling position. Thus, the clutch mechanism 31 enters a normal clutch connection state in which the rotation of the motor 24 is transmitted to the fixed gear body 69, and the armature 61 is moved from the normal clutch connection position to the clutch disengagement direction by the elasticity of the clutch release spring 70. The transition before being disengaged from the fixed gear body 69 during return The movable gear body 65 can be held in a brake clutch coupling position where the movable gear body 65 and the fixed gear body 69 are continuously engaged with each other by contacting the gear body 65 and the clutch mechanism 31 can be brought into a brake clutch coupled state. A clutch holding surface 64D is provided, and the contact between the clutch holding surface 64D and the moving gear body 65 causes the armature 61 to rotate together when the moving gear body 65 rotates when the electromagnetic coil section 60 is off. The control unit 88 that controls the motor 24 and the electromagnetic coil unit 60 keeps the electromagnetic coil unit 60 on and restricts the co-rotation state of the moving gear body 65 and the armature 61. The motor 24 is rotated in the reverse direction to release the contact between the moving gear body 65 and the clutch holding surface 64D, and then the electromagnetic coil section 6 0 and a clutch mechanism of a power unit provided with a normal clutch coupling power release control for turning off the motor 24. A wheel 26 that rotates around the support shaft 28 by the power of the motor 24, a fixed gear body 69 supported by the support shaft 28, and a normal clutch engagement position when the wheel 26 moves to the clutch coupling position, meshes with the fixed gear body 69 and the wheel 26. A rotation gear that can be transmitted to the fixed gear body 69 and disengaged from the fixed gear body 69 when moved to the clutch disengaged position, and a clutch that urges the movable gear body 65 toward the clutch disengaged position. In the clutch mechanism 31 including the release spring 70, the moving gear body 65 can receive the rotational force of the motor 24 via the wheel 26 even if it moves in either the clutch connecting direction or the clutch disengaging direction. And the clutch mechanism 31 is further rotated relative to the moving gear body 65 to engage the clutch mechanism 31. An armature 61 capable of displacing the movable gear body 65 to the clutch coupling position against the elasticity of the hose release spring 70, and applying a brake resistance to the armature 61 by attracting the armature 61 by a magnetic force, the armature 61. And an electromagnetic coil portion 60 that can regulate the co-rotation state of the movable gear body 65. When both the motor 24 and the electromagnetic coil portion 60 are turned on, the movable gear body 65 is displaced to the normal clutch coupling position. Thus, the clutch mechanism 31 is in a normal clutch engagement state in which the rotation of the motor 24 is transmitted to the fixed gear body 69, and the movable gear body 65 is connected to the movable gear body 65 by the elasticity of the clutch release spring 70. Engagement with the fixed gear body 69 on the way back from the coupling position in the clutch disengagement direction Before coming off, the armature 61 is brought into contact with the armature 61 so that the movable gear body 65 can be held at a brake clutch coupling position where the meshing of the movable gear body 65 and the fixed gear body 69 is continued, and the clutch mechanism 31 is coupled to the brake clutch. A clutch holding surface 72D that can be brought into a state is provided, and the contact between the clutch holding surface 72D and the armature 61 causes the armature 61 to rotate together when the moving gear body 65 rotates when the electromagnetic coil portion 60 is off. And the control unit 88 that controls the motor 24 and the electromagnetic coil unit 60 keeps the electromagnetic coil unit 60 on and restricts the co-rotation state of the moving gear body 65 and the armature 61. The motor 24 is rotated in reverse to release the contact between the armature 61 and the clutch holding surface 72D. A clutch mechanism of a power unit provided with a normal clutch coupling power release control for turning off the electromagnetic coil unit 60 and the motor 24 thereafter. 3. A clutch mechanism for a power unit according to claim 1, wherein the fixed gear body 69 is connected to a wire drum 30 that slides the vehicle slide door 11 through a wire cable when the fixed gear body 69 rotates.

Images