JP2717098B2 - Door lock device - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a door lock device in which meshing between a worm gear and a wheel gear constituting an actuator is improved.

(Prior Art) An electric motor is used to lock or unlock a door lock. An actuator that performs such an operation includes a worm gear fixed to the electric motor, and a wheel gear that meshes with the worm gear. The rotation of the wheel gear causes the operation lever to rotate via the projection.

(Problems to be Solved by the Invention) In both the locked and unlocked positions, regardless of the direction of the tooth streaks, the reaction force acting on the convex portion of the wheel gear causes the meshing reaction force to reduce the meshing of the wheel gear. In order to prevent the displacement, the position where the motor should be disposed is limited to a position at half the operating angle of the wheel gear, and is not applicable because the operating angle is small. If the rotation shaft of the wheel gear is inserted into a resin housing or if the wheel gear is made of resin, sufficient flesh must be used to prevent elastic deformation when the aforementioned meshing reaction force acts, and Materials that are excellent in high-temperature characteristics are required, and it is difficult to realize the door lock position due to the space inside the door, the cost, etc. In addition, the restriction on the motor position is a compact suitable for the arrangement inside the door. This makes the actuator design impossible.

Therefore, an object of the present invention is to solve the above-mentioned problem.

(Means for Solving the Problems) In order to solve the above-described problems, the present invention provides a worm that is rotationally driven by a motor, a wheel gear that meshes with the worm, a convex portion provided on the wheel gear, Actuating lever with an abutting arm, when the movement of the operating lever is restricted by the stopper at the lock and unlock positions, the protrusion of the wheel gear and the arm abut against the line connecting the wheel gear rotation center and the worm Then, the tooth streak is determined so that the elastic deformation of the wheel gear generated by the meshing reaction force is displaced toward the axial base of the wheel gear, and the displacement of the wheel gear toward the axial tip end at the other position is determined. Provided is a door lock device characterized in that the door lock device is prevented by a reaction force acting on a convex portion of a wheel gear and maintains a normal meshing state.

(Operation) When the stop position of the operating lever is near the line connecting the worm gear and the shaft, and the contact point between the convex portion of the wheel gear and the arm is located, the engagement is caused by the component force generated by the driving force from the worm gear. By deciding the tooth streak in the direction that does not become shallow, it is possible to obtain freedom in the arrangement of the operating lever, the wheel gear, the worm gear, and the like, and a compact door lock power actuator unit can be realized.

(Example) An example in which the concept of this example is applied to a door lock device will be described below. The door lock device 1 has a substantially L-shaped release lever 3 pivotally supported by a main housing 2 made of synthetic resin.
The release lever 3 is rotatable about a fulcrum 61 at the center thereof. The fulcrum 61 is also the center of rotation of the pole of the door lock operating portion including a latch and a pole (not shown). The release lever 3 is interlocked with the ball via the pin 62. When the door is open, a striker (not shown) attached to the vehicle engages with the latch, and the pole engages with the latch. The release lever 3 shown in FIG. 1 is in a meshing state in which the latch of the door lock and the pawl are engaged with each other. By rotating the release lever 3 counterclockwise, the pawl rotates the latch, and A latch release state in which the engagement of the pawl is released is obtained, and the door can be opened. When the outside handle is operated, a force acts in the direction indicated by 29, and the rod 4 rotates the lever 30 pivotally supported by the main housing 2 counterclockwise about the fulcrum 31. When the inside handle is operated, a force acts in the direction indicated by 28, and the lever 30
Rotate counterclockwise around 31. The counterclockwise rotation of the lever 30 pushes down the open lever 5 pivotally attached to one end of the lever 30. The downward movement of the open lever 5 is caused by the projecting piece 6 at the center of the open lever 5.
Pushing the end 7 of the release lever 3 and rotating the release lever 3 counterclockwise around the fulcrum 61, the door lock operating part is brought into a latch release state in which the latch and the pawl are disengaged, and the door can be opened. (See FIG. 2).

The door is locked to prevent the door from being inadvertently opened while the vehicle is running. In general, the door is locked by pressing a locking button 8 and rotating a locking arm 9 interlocked therewith in a clockwise direction. Make this door lock. A part of the locking arm 9 is connected to a lower portion of the open lever 5 through a long hole. When the locking arm 9 is in the position shown in FIG. 1, the lowering of the open lever 5 allows the protrusion 6 to abut the end 7 of the release lever 3. However, when the locking button 8 is pressed and the locking arm 9 is rotated clockwise about the pin 10 together with the pin, the open lever 5 moves in the direction of arrow C,
Release the protruding piece 6 from the end 7 of the release lever 3 (third
See figure). As a result, even if the open lever 5 is lowered by operating the steering wheel, there is no hit between the protruding piece 6 and the end portion 7, and the door lock is kept engaged (see FIG. 4). .

The keyless lock mechanism will be described. With the door open, the locking button 8 is pressed to rotate the locking arm 9 clockwise so that the protruding piece 6 does not face the end 7 of the release lever 3. When the outside or inside handle is operated, the open lever 5 is pushed down, and the state shown in FIG. 5 is obtained. When the door is closed in this state, the release lever 3 is turned counterclockwise. However, the end 11 of the open lever 5 and the projecting piece 12 of the release lever 3 are hit without hitting, and the release lever 3 can be freely rotated counterclockwise. In this direction, maintaining the door locked (see FIG. 6). After the door is closed, the release lever 3 is brought into the state shown in FIG.
When the operation from the handle side is stopped, the state returns to the state shown in FIG.

Next, the self-cancelling mechanism will be described. While the door is open, the locking button 8 is pushed, the locking arm 9 is turned clockwise, and the open lever 5 is turned in the direction C shown in FIG. I do. When the door is closed without operating the outside or inside handle, the release lever 3 is rotated counterclockwise by a pole of a door lock operating portion (not shown). This movement causes the projecting piece 12 of the release lever 3 to abut on the step 11 of the open lever 5 to rotate the open lever 5 clockwise as shown in FIG. As a result, the locking button 8 is returned to the original position and the locking arm 9 is returned.
Rotates counterclockwise about the pin 10 through the elongated hole of the open lever 5. That is, since the state returns to the state shown in FIG. 1, when the door is opened by operating the handle, the protruding piece 6 of the open lever 5 pushes down the end 7 of the release lever 3 to open the door. Lock state.

The key operation will be described with reference to FIG. 1, FIG. 9 and FIG. The key operation lever 13 is rotatably supported on the sub-housing 2 ′, and its projection 14 is arranged in parallel with the projection 15 of the locking arm 9. This lever 13 is connected at one end to a key cylinder via a rod. When the key is operated in the locking direction, the key operation lever 13 rotates clockwise from the position A to the position B, and the locking arm 9 is rotated clockwise by the contact between the protrusion 14 and the protrusion 15, When the door lock is locked and the key operation is stopped, the key operation lever is actuated by the action of the spring attached to the key cylinder.
13 returns from B to A. That is, the locking button 8
Is pressed down, in other words, the protruding piece 6 of the open lever 5 and the end 7 of the release lever 3 are not opposed to each other, and the door remains closed even if the outside or inside handle is operated. Well. When the key is rotated in the unlocking direction, the step 14 'pushes the projection 15 and the locking arm 9
Is turned counterclockwise to the unlocked state shown in FIG. In addition, in the state of FIG.
Even if 13 is rotated to the position of B ', only the step 14' comes close to the projection 15, and the locking arm 9 does not rotate.

In addition to the manual operation described above, the pin 10 is electrically rotated in response to an instruction signal from the driver, and the locking arm 9 is rotated clockwise (or vice versa) to change the lockable and unlockable state. The gain is made. Please refer to FIG. An operating lever 17 having an arm 16 is fixed to the pin 10. A wheel gear 18 is rotatably supported by the sub-housing 2 ′, and a downward arm 16
Are opposed to both ends 19 and 20 of the convex portion 45 erected on the wheel gear 18.

On the other hand, an annular groove 21 is provided in the bottom plate portion of the sub housing 2 '. As shown in FIG. 10, the groove 21 is partially narrowed by wall surfaces 22 and 23 facing each other. The coil spring 24 is inserted into the groove 21, and its end is brought into contact with the shoulders of the wall surfaces 22 and 23. Further, a projecting piece 25 projecting from the lower surface of the wheel gear 18 is located between the wall surfaces 22 and 23. As a result, for example, when the wheel gear 18 rotates clockwise in FIG. 10, the protruding piece 25 contracts the spring 24 while pressing the right end of the spring 24. At this time, the left end of the spring 24 is a wall
It abuts on the shoulders of 22, 23 and allows the spring 24 to compress. The rotation of the wheel gear 18 is such that the end 19 of the convex portion 45 abuts on the arm portion 16, the rotation of the operating lever 17 and the pin 10 is performed, and the locking arm 9 can be moved from the position A to the position B. To The rotation of the wheel gear 18 in the opposite direction
However, the spring 24 is compressed in the counterclockwise direction while the right end of the spring 24 abuts against the shoulders of the wall surfaces 22 and 23, and the operating lever 17 and the pin 10 are rotated by the end 20 to move the locking arm 9 to the B position. To the A position. The use of such an annular groove 21 increases the overall length of the spring 24 and ensures sufficient deflection.

Wheel gear 18 rotatably supported by the housing
Engages with the worm gear 27 directly connected to the electric motor 26, and the rotation direction of the wheel gear 18 is controlled by controlling the power supply to the motor 26. Generally, the worm gear advance angle γ ₀
However, when the friction angle becomes larger than φ, the transmission of the rotational torque from the wheel gear 18 to the worm gear 27 becomes possible. Therefore, in this example, the advance angle is set to be equal to or more than the friction angle (φ = 8.53 °) by utilizing the relationship of μ (friction coefficient) = tan φ. That is, the friction coefficient μ of the worm gear 27 made of phosphor bronze and the wheel gear 18 made of resin is 0.1 to 0.15, and the friction angle φ is 5.71.
The friction angle is set to 8.53 or more, and the rotation of the worm gear 27 from the wheel gear 18 is enabled. Such setting of the advance angle (γ ₀ ) of the worm gear 27 is performed, for example, by turning the wheel gear 18 by the spring 24 immediately after the operation, even if the driver rotates the wheel gear 18 by a door lock operation using the electric motor 26. It is possible to return to the original position, and then to enable manual operation. In other words, manual operation can be performed after manual operation or electric operation or electric operation. In addition, since the operation lever 17 and the wheel gear 18 are completely separated at the time of manual operation, the arm portion 16 only runs idle between the two end portions 19 and 20 of the pair of the convex portions 45, and the motor portion can be dragged. It can be operated lightly and has a good operation feeling.

As shown in FIG. 12, the pin 10 fixed to the operating lever 17 operated by the motor 26 in the sub-housing 2 '
Has a stepped portion and a square portion at the tip thereof, and is inserted into the stepped hole 32 of the sub housing 2 '. The outer peripheral surface of the stepped hole 32 is a bearing portion 34 that receives the hole 33 of the key operation lever 13 on the outer peripheral surface. When the pin 10 is inserted into the bearing portion 34, the square portion of the pin 10 protruding from the bearing portion 34 is inserted into the same hole 35 of the locking arm 9 and fixed by caulking or the like. Further, the locking arm 9 is seated on the top surface of the bearing portion 34. Bearing part 34 for key operation lever 13 is attached to main housing 2
Because it is formed integrally with the bearing, there is no need for a separate bearing,
Further, the mounting portion of the locking arm 9 does not protrude outward.

The ends of the turnover spring 36 for holding the locking arm 9 in the locked and unlocked positions are shown in FIGS.
As shown in the figure, a recess 37 of the main housing 2 near the bearing portion 34 and a hole 38 of the locking arm 9 substantially facing the recess 37 are engaged. In this example, since the pin 10 is directly connected to the locking arm 9, the operating force for efficiently transmitting the rotational force from the motor to the turnover spring can be reduced. This reduces the size of the motor 26 and makes the overall device more compact.

As already understood from the description of FIG. 1, the fulcrum 61 serving as the rotation center of the release lever 3 also serves as the rotation center of the pole of the door lock operating portion (not shown). The door lock operating portion is moved to the latch release position, and thus the door lock operating portion is accommodated in the main housing 2. The various levers and arms as described above are disposed on the outer surface of the main housing 2. On the other hand, the pin 10 serving as an output shaft including the motor 26, etc.
Is accommodated in an extension of the main housing 2 for the door lock operating portion. Further, the electric motor 26 rotates the operating lever 17 to move the locking arm 9 to the locked position (B) and the unlocked position (B ') shown in FIG. ′) Is provided with a stopper 39 for stopping the operation lever 17. The function of the stopper 39 will be described with reference to FIG. Although only one stopper 39 is shown in FIG. 14, the function of the other stopper is the same, so that the drawing and its description are omitted.

The operation of the electric motor 26 rotates the wheel gear 18 via the worm gear 27 and rotates the operation lever 17 together with the pin 10 by the end 19 of the projection 45. At this time, the return spring 24 bends and stores energy for returning the wheel gear 18 to the neutral position. In this example, when the operating lever 17 comes to the regular stop position 63, the operating lever 17 and the stopper 39 come into contact with each other and try to prevent the movement of the operating lever 17,
The operating lever 17 moves to the overtravel position 64 while elastically deforming the stopper 39 by the rotational inertia force of the motor. That is, the stopper 39 is elastically deformed by an amount corresponding to the overtravel. The stopper 39 is formed of a solid or hollow body such as rubber, synthetic resin, or the like that allows such elastic deformation. The elastic force of the stopper is used when the electric motor 26 is turned off, that is, when the wheel gear is returned to the neutral position. It functions to push the operating lever 17 back together with the spring 24 to the proper locked and unlocked position. The assisting force from the stopper 39 can reduce the urging force of the spring 24 and the output of the electric motor 26 accordingly. FIG. 15 shows the relationship between the wheel gear 18 and the motor reverse rotation torque.

FIG. 12 shows the relationship between the pin 10 and the main housing 2, which will be described in more detail with reference to FIG.

The pin 10 serving as an output shaft fixed to the operation lever 17 has a stepped configuration including a large shaft diameter portion 40 and a small shaft diameter portion 41. On the other hand, the hole 32 of the sub-housing 2 '
And a small opening 43 for receiving the small shaft diameter portion 41. The locking arm 9 is fixed to a small shaft diameter portion 41 protruding from the sub-housing 2 ', and the key operation lever 13 is rotatably supported on the bearing 34 of the sub-housing 2'.

When mounting the hole 32 of the sub housing 2 'of the pin 10,
The O-ring 44 is fitted to the small shaft diameter portion 41 of the pin 10, and the output shaft 10 is inserted into the hole 32 from the inside of the sub housing 2 'so that the small shaft diameter portion 41 projects from the sub housing 2'. Hole 32
Insertion of the output shaft 10 into the hole 10 causes the step of the hole 32 to face the step of the pin 10 via the O-ring 44. Thus,
The movement of the pin 10 with respect to the sub housing 2 'can be restricted. This is useful for ensuring correct movement of the operating lever 17. Also, since the O-ring 44 is attached to the pin 10 and the O-ring 44 may be attached to the hole 32 of the sub-housing 2 ', the assembling operation is very easy.

In the example shown in FIG.
As shown in FIG. 17 and FIG. 17, a semicircular arc-shaped projection 45 is provided on the wheel gear 18, but a pair of pins may be erected on the wheel gear 18 instead. The ends 19 and 20 of the convex portion 45 can freely contact the arm 16 of the operating lever 17. Electric motor 26
When power is supplied to the wheel gear 18 via the worm gear 27
Rotates. Convex part 45 according to the rotation direction of wheel gear 18
One end of the lever abuts on the arm 16 to move the operating lever 17 to the locked or unlocked position while compressing the return spring 24, and the pin 10 serving as the output shaft moves the link mechanism. When the operating lever 17 occupies the locked or unlocked position and the power to the motor 26 is turned off, the release biasing force of the compressed return spring 24 causes the wheel gear 18, the worm gear 27 and the motor 26 to rotate in reverse, and the wheel gear 18
To the neutral position. When the wheel gear 18 returns to the neutral position, a gap 46 is left between the end of the projection 45 and the arm 16 as shown in FIG. This gap 46, when the electric motor 26 is energized, immediately rated the rotation speed of the motor,
When the projection 45 comes into contact with the arm 16 of the operation lever 17, the inertia energy of the motor output shaft increases the inertia of the speed reduction unit and the static friction of the door lock mechanism and the like. That is, the projection 45 is the operating lever
When the arm 17 comes into contact with the arm 16, the rotational inertia energy of the motor can be transmitted to the arm 16, so that the size of the motor can be reduced.

Although the door lock device 1 has been described, the mounting portion of the door lock device 1 will be described with reference to FIG. The vehicle has a center pillar 49 between a front door 47 and a rear door 48, and a hinge 50 and a striker 51 for the rear door 48 are fixed to the center pillar 49. When the front door 47 is opened and closed, the striker 51 is detachable from a ratchet (not shown) of the door lock device 1. on the other hand,
When the window glass 52 of the front door 47 moves up and down, it moves along the locus 53 along the center pillar 49. Therefore, the door lock device 1 fixed to the front door 47 side
Avoid the trajectory 53 of the wind glass 52
It is necessary to prevent interference between the door lock device 1 and 52. In order to avoid such interference, a concave portion 54 recessed rearward is formed at the front edge of the center pillar 49, and an overhang 55 is formed at the rear edge of the front door 47. The lock device 1 is stored. That is, the door lock device 1 needs to have an external shape that fits in the limited space of the overhang portion 55. In addition, the shapes of the overhang portion 55 and the concave portion 54 are as follows.
It is designed not to interfere with the lower hinge 50 of the rear door 48. In this example, the rear edge of the front door 47 has a shape indicated by 113.

As is apparent from FIG. 16, in this example, the lower portion of the main housing 2 is extended, and the actuator is supported by the sub-housing 2 'in order to arrange the electric actuator on this extension. It is fixed to the housing 2. The main housing 2 housed in the overhanging portion 55 of the limited space described above has a shape extending forward at the lower portion.

Referring to FIG. The mating surface 115 of the sub-housing 2 ', which is fitted to the main housing 2 whose lower part is bent forward, is formed in a straight line inclined with respect to the mounting surface 116 of the door lock device 1 in order to enhance the sealing property therebetween. In order to further improve the sealing performance of the two housings 2 and 2 ', that is, to prevent the mating surface 115 of the two housings 2 and 2' from shifting,
As shown in FIGS. 17, 22 (a) and 23, a pair of hooks 117 is provided at the lower portion of the sub-housing 2 '.
17 is brought into contact with the lower end surface of the main housing 2. Hook 117
Abutment on the lower end surface of the main housing 2 (see FIG. 20)
It prevents the displacement of the two housings 2 and 2 ′ at the time of fastening, thereby improving the sealing performance, and further prevents the center deviation between the pin 10 serving as the output shaft and the pin receiving hole of the main housing 2.

Referring back to FIG. A substantially U-shaped groove 118 is arranged along the inner edge of the main housing 2, and a rubber O
-Insert the ring 119 and bend the O-ring 119 by the mating surface 115 of the sub-housing 2 'to secure the sealing pressure. The inner edge of the main housing 2 is a wall 120 extending upward, and even if rainwater or dust passes through the O-ring 119, the wall 120 prevents rainwater or dust from entering the main housing 2. Let it. This wall 120 is provided on both housings 2,
It is also effective in improving the sealing performance when the 2 'mating surface is bonded or welded.

As described above, the shape of the housing has a substantially rectangular shape with the lower part protruding forward of the vehicle, so that the operating lever 17 is moved from the shaft 121 fixed to the output shaft 10 as shown in FIG. A contact 123 extending to the left of the paper and detecting a locked or unlocked state in cooperation with a substrate 122 fixed to the main housing 2.
, A step portion that connects the arm portion 124 and the arm portion 16 arranged so as to avoid interference with the housing lower shape.
It has 125.

A ring-shaped convex portion 126 is formed on the side of the shaft portion 121 that comes into contact with the bearing surface of the sub-housing 2 ′ to facilitate dimensional control in the thrust direction and reduce the contact surface with the sub-housing 2 ′. Grease retention while reducing rotational resistance
127 are formed.

Further, the arm portion 16 is slidably supported by a convex portion 128 provided on the main housing 2 to prevent an increase in rotational resistance due to the entire contact between the arm portion and the housing.

The contact 123 is provided with a fixed portion attached to the projection 129, 129 'provided on the arm portion 124 of the operating lever 17, and contact portions 130, 130' sliding on the substrate 122. A locking portion is provided to prevent the arm from coming off.

 FIG. 21 shows the operating state of the switch diagram.

The substrate 122 is made of an insulator such as an epoxy resin,
Conducting portions 131 and 131 'made of copper or the like are arranged in the passing portions of the contact portions 130 and 130'.

In the embodiment, when the conducting portions 131 and 131 'are in contact with the contact portions 130 and 130' and the detection circuit is opened, the unlocked state is set, and when the detection circuit is closed, the locked state is set.

As described above, since the switch is disposed on the operating lever 17 directly connected to the locking arm 9 for switching between locking and unlocking, the position detection accuracy is improved, and further, the substrate 122 fixed to the main housing 2 is removed. Since the arrangement is made so as not to overlap with the projection 129 for fixing the contact 123 of the arm part 124 of the operating lever 17, the substrate and the arm part can be brought as close as possible, and the height of the driving part can be reduced. .

Please refer to FIG. 22 and FIG. When a seal 189 made of rubber or the like that is attached to the door panel 187 with a clip 188 and that seals between the door and the body is disposed so as to pass over the actuator part of the door lock, the tip 190 of the clip 188 is used. Interference with the robot becomes a problem.

In this embodiment, attention is paid to a void formed above the motor housing portion of the main housing 2, and a concave portion 191 that is as concave as possible is provided to secure a gap between the clip 188 and the tip 190.

By providing a concave portion for avoiding interference with the front end of the clip on the actuator portion shaped in a substantially rectangular shape in this way, the rear edge 113 of the door panel and the vertical movement locus 114 of the door glass shown in FIG. Thus, a substantial required space can be reduced, and a compact door lock having a high degree of freedom in arrangement on a vehicle can be obtained.

In the embodiment shown in FIG. 22, the fastening between the two housings 2 and 2 'is performed by a screw 192.

As shown in FIGS. 17, 24 and 25, a hole 193 larger than the outer diameter of the screw 192 through which the screw 192 passes is provided in the sub-housing 2 ', and the outer diameter of the screw 192 is provided in the main housing 2. A slightly smaller fastening hole 194 is provided.

Referring to FIG. In order to prevent the relationship between the two housings 2 and 2 'from shifting due to the fastening, the holes of the sub-housing 2' arranged diagonally are made holes 195 slightly smaller than the outer diameter of the screw 192, and the screw 192 is tightened. At times, the screw shaft center and the hole center coincide with each other.

In this way, the inexpensive and space-saving centering structure can reduce the power loss at the bearing of the pin 10 caused by the displacement between the main and sub-housings 2 and 2 ', and also reduce the motor output. The motor can be downsized and smooth and quiet operation can be obtained.

 Refer to FIG. 17, FIG. 24, and FIG.

The stopper of the sub-housing 2 'so that the stopper 39 held by the stopper holding portion 196 of the main housing 2 does not come off.
A retainer 197 is provided at a position facing 39.

In this manner, by providing the stopper 197, the shock load including the rotational inertia load of the motor is applied to the stopper 39 via the operating lever at the locked and unlocked positions, and elastically deforms. Since the stopper 197 is prevented from coming out of the 196, the holding of the stopper 39 can be guaranteed against repeated loads, and stable performance can be maintained for a long period of time.

Further, since the stopper portion is housed between the main and sub housings 2 and 2 ', the performance of the stopper rubber does not decrease due to the adhesion of foreign matters such as rainwater and dust, and the durability is excellent.

With reference to FIG. 16 and FIG. 28, the venting of the air in the housing will be described. An air hole 107 formed in cooperation with the sub-housing 2 ′ is provided at the lower end (left side in the drawing) of the main housing 2, and a negative pressure is generated in the housing due to a change in environment, for example, a change in temperature. The shape of the air hole 107 is such that rainwater or the like adhering to the outer periphery is not sucked into the inside. The air hole 107 is provided with a wall 109 facing the opening 108, and the air hole is substantially U-shaped by the wall 110 facing the wall 109. And the size of the hole is determined by the side walls 111 and 112.
And are formed in a substantially square shape. Therefore, the opening 10
Even if water drops such as rainwater adhere to the vicinity of 8 or dust is present, the two walls 109 and 110 do not enter the main housing 2.

The drainage from the housing will be described with reference to FIGS. 16 and 29.

A cavity 179 formed between the main housing 2 and the door lock plate 178 abutting on the door lock mounting surface 116 of the door panel accommodates a well-known engagement mechanism for maintaining the door lock state of the door lock.

In the lower part of the empty space 179, a groove 180 formed between the plate 178 is provided for draining rainwater or the like,
It extends as far as possible below the plate 178.

In the lower part of the groove 180, a water passage 182 is formed with the bearing 181 of the pin 10 as close to the door panel 113 as possible,
The groove 180 is substantially terminated by the wall 183.

In this way, by providing the wall 183 that restricts the groove 180, the thickness of the door lock actuator unit in the vehicle longitudinal direction can be reduced, a gap between the door lock actuator 114 and the elevating locus 114 can be ensured, and the door lock device It can be placed at a higher position to improve the strength of the upper part of the door against collisions, etc. Or it can be placed behind the door from the elevating trajectory, increasing the door glass area and increasing the design freedom Can be.

Referring to FIG. 16 again, the periphery of the axis 100 will be described.

The wheel gear 18 is rotatably mounted on a shaft 100 inserted in the sub-housing 2 ′, and the movement in the pulling-out direction is regulated by a washer 101 caulked at the tip of the shaft 100.

A washer 102 is inserted between the wheel gear 18 and the sub-housing 2 'in order to reduce the resistance during rotation, thereby preventing contact between the resins.

The contact surface between the wheel gear 18 and the washer 101 is formed with a ring-shaped convex portion 103, which facilitates dimensional control in the thrust direction, reduces the contact area with the washer 101, and reduces rotational resistance. A grease stay 104 is formed.

The portion of the shaft 100 inserted into the sub-housing 2 'increases the strength against bending and rotation of the shaft 100 caused by the engagement between the worm gear 27 and the wheel gear 18, and also improves the holding strength in the thrust direction. To make the axis 10
0 and the other end 10 for receiving the tip and washer 101 when caulking
5 protrudes outside from the surface of the sub housing 2 ',
A brim section 106 is provided to lengthen a path when rainwater or the like invades from the increase in the amount of water and to prevent rainwater from entering.

FIG. 17 is a view as seen from the inside of the sub-housing 2 ', showing the pin 10, the operating lever 17, the wheel gear 18, the motor 2
6. The positional relationship between the worm gear 27 and the worm gear 27 is shown in FIG.
18 is supported by an inserted shaft 100, and the worm gear 27 and the motor 26 are supported by supports 132, 133, and 134 provided on the sub-housing 2 '. , 136.

Thus, the positional relationship of the drive transmission system, especially the wheel gear
Since the meshing relationship between the worm gear 18 and the worm gear 27 is determined only by the sub-housing 2 ', manufacturing errors such as the distance between the gear pitches can be minimized, and smooth power transmission becomes possible. As the loss is reduced, the size can be reduced.

 The motor support structure will be described in detail with reference to FIG.

A case 137 made of a steel plate and formed by deep drawing is fixed to a case 138 made of resin or the like by a claw portion 139.

The motor shaft 140 is rotatably supported by a bearing 141 fixed to the bearing 137 'of the case 137 by press fitting and a bearing 142 fixed to the bearing 138' of the case 138 by press fitting.

A core 145 holding a commutator unit 143 that receives supply of electricity from the outside and a winding 144 is fixed to the motor shaft 140.

Also, in order to prevent interference between the winding 144 and the case 137,
A collar 146 is disposed between the collar 146 and the core 145. magnet
148 is fixed to case 137.

One end 147 of the motor shaft is processed into a spherical shape, and the metal thrust plate 1
Supported by 49.

This thrust plate 149 resists the load when the worm gear 27 is press-fitted and fixed to the knurl 151 provided at the other end 150 of the motor shaft, prevents the resin case 138 from cracking, and operates when locking and unlocking. It is effective for receiving the generated thrust load and improving the durability.

The support portion 133 supporting the bearing portion 137 'of the case 137 and the support portion 132 supporting the bearing portion 138' of the case 138 determine the thrust position of the motor and the positional relationship with the shaft 100 pivotally supporting the wheel gear 18. decide.

Next, a shaft part whose tip of the worm gear 27 is machined into a spherical shape
The support 134 supporting the 152 will be described.

The motor shaft 140 is movable in the thrust direction by a distance 153 provided between the collar 146 and the bearing 141.

In addition, a load is applied to the motor shaft 140 in a direction of entering the motor case, and one end 147 of the motor shaft
When rotating in contact with 49, it is in contact with the spherical surface, so the rotation resistance is small and it can rotate with a light torque.

Conversely, when a load is applied in the direction in which the motor shaft is pulled out, the end surface of the collar 146 comes into contact with the end surface of the bearing 141, the rotation resistance is large, and a large torque is required to rotate the motor shaft.

As in the embodiment, in the worm meshing, a load is applied in the direction of pushing or pulling out the shaft in any of the forward and reverse directions, and the output of the motor needs a large output in consideration of the above-mentioned large rotational resistance. Become.

Further, when the power supply is cut off after driving the motor, the wheel gear 18
, And the worm gear 27 is rotated to return to the neutral position, the return spring output must be increased due to the large rotational resistance of the motor shaft, and the motor output is increased accordingly. Is required. As described above, in order to prevent contact between the collar 146 and the bearing 141, which causes various output losses, a motor shaft length 154 is provided between the spherical end portion 152 of the worm gear 27 and the support portion 134. A gap 156 between the collar 146 and the end face of the bearing 141 is smaller than a gap 153 between the collar 146 and a gap between the collar 146 and the end face of the bearing 141, while absorbing a manufacturing error with the length 155 to the thrust load receiving surface of the support portion 134.

Therefore, even if the motor shaft 140 moves in the direction in which the motor shaft 140 is pulled out of the case, the spherical end of the shaft portion 152 of the worm gear 27 comes into contact with the support portion 134, and the collar 146 and the bearing 141
The contact between the motor and the end faces is avoided, so that an increase in rotational resistance can be prevented, the loss of motor output is prevented, and the size of the motor can be reduced.

The manufacturing error between the support portions 132 and 133 is set in the direction in which the motor case and the gap occur because the elastic deformation of the support portion 133 does not absorb the manufacturing error. Perform so that 132 contacts.

Also, in the radial direction of the shaft portion 152 of the worm gear 27, a small clearance is set between the support portion 134 and, for example, the operating lever is stopped at the lock and unlock positions, and the pitch is generated by the reaction force engaged with the wheel gear 18. It comes into contact when the distance is about to increase.

When the power to the motor is cut off and the return spring 24 drives the wheel gear 18 to rotate the worm gear 27 and return to the neutral position, the contact between the support portion 134 and the shaft portion 152 is released, There is no loss of the return spring force at this portion, and therefore the return spring force can be reduced, and the size of the motor can be reduced. The normal motor shaft is determined by the support
132 and 133, manufacturing errors can be easily absorbed, and an inexpensive housing can be obtained.

Next, the main housing 2 is provided with the following support portions, respectively. That is, as shown in FIG.
A support portion 157 is provided which comes into contact when the 152 is displaced.

As shown in FIG. 32, a support 158 for supporting a bearing 137 'of the motor case 137 is provided.

As shown in FIG. 33, an elastic body 159 such as a sponge is provided on the main housing 2 side of the motor case 137 supported by the sub housing 2 'in a bent state.
When the dimension between the main housing 2 and the main housing 2 can be widened, or when the dimension 160 between the support portions 132 and 133 can be increased to cause a gap between the main housing 2 and the motor case, opening and closing the door, The motor case is prevented from moving and generating abnormal noise due to vibration during running or a worm meshing reaction force when the motor is driven.

As shown in FIG. 34, a support 161 for supporting a bearing 138 'of the motor case 138 is provided.

Next, the worm gear 27 fixed to the motor shaft 140,
The engagement with the wheel gear 18 that engages with this gear will be described.

FIG. 35 shows a standard meshing state between the worm gear 27 and the wheel gear 18. 162 is a tooth of a wheel gear, 163 is a tooth of a worm gear, and 164 is a backlash in a standard time. The shape of the wheel gear 18 has a complicated shape as shown in FIGS. 16 and 17, and is therefore made of resin. In the case of such a complex shape having an indeterminate wall pressure, distortion of the outer shape due to molding is inevitable, and when the tooth width is increased, the backlash is reduced and smooth tooth engagement operation is not possible. In the case of occurrence, a load is applied to the tooth tip, resulting in a decrease in strength.

Generally, in order to increase the backlash, a method of setting the distance between pitches larger than a standard value, as shown in FIG. 36, is used.
In the case of 1.35 mm), the distance between the pitches can be increased only by a small amount, and a predetermined backlash amount cannot be obtained.
In addition, since a load is applied to the tooth tip more, especially in the case of driving a lever or the like which is brought into contact with a fixed object after a predetermined operation, the rotation of the motor is suddenly stopped at the time of the stop, so that the motor An impact load containing the rotational inertia energy is applied, and the teeth themselves are damaged.

In the present embodiment shown in FIG. 37, a wheel gear made of resin is used.
The tooth profile and the pitch distance of 18 are standardized, and the backlash is increased by transversally shifting the teeth of the worm gear 27 made of phosphor bronze, which has a relatively large strength. Numeral 165 indicates a worm gear tooth having a reduced tooth width at the lateral displacement, and numeral 166 indicates an increased backlash at the lateral displacement. As described above, since the pitch distance is standard, it is possible to prevent contact at the tooth tip, to reduce the loss in strength, and to absorb the distortion of the teeth of the wheel gear.

Next, the relationship between the tooth streak direction and the operation lever will be described in detail.

FIG. 38 shows a state in which the convex portion 45 of the wheel gear 18 meshed with the worm gear 27 abuts on the arm 16 of the operating lever 17 by the drive of the motor, and the lever 17 has moved to the unlock position where it abuts the stopper 39. Show. FIG. 39 shows a state in which it has similarly moved to the lock position.

In FIG. 38, 167 is a wheel gear 1
The driving force given to 8 is shown. 168 indicates a reaction force from the stopper 39 to the operating lever 17, and 169 indicates a reaction force from the arm 16 to the end of the convex portion 45. FIG. 40 is an H view of FIG. 38, in which the wheel gear 18 is provided with upper right teeth 170 on the paper surface. The driving force 167 applied from the worm gear 27 generates a component force 171 that is directed upward on the paper surface due to the inclination of the teeth 170 in the case of a toothed streak as shown. FIG. 41 is a view as viewed in the direction J of FIG. 38. In the case where the aforementioned component force is 171, the resin wheel gear is elastically deformed in the direction in which the meshing with the worm gear becomes shallower, in the counterclockwise direction on the paper, or the width of 100 mm. Although the insert portion is elastically deformed, the engagement between the wheel gear and the worm gear is prevented from becoming shallow due to the reaction force 169 acting on the convex portion 45 that generates a drag in the clockwise direction on the paper.

In FIG. 39, 172 is a wheel gear 1 from the worm gear 27.
8 indicates a driving force, 173 indicates a reaction force from the stopper 39 to the operation lever 17, and 174 indicates a reaction force from the arm 16 to the projection 45.

42 is a K view of FIG. 39, in which the driving force 172 applied from the worm gear 27 is a component force 175 that is directed downward on the paper surface.
Generate.

FIG. 43 is an L view of FIG. 39.
The wheel gear or the insert portion of the shaft 100 is elastically deformed in the direction in which the engagement with the worm gear becomes deeper, or in the clockwise direction on the paper.

When the operating lever 17 is stopped by the stopper 39, the contact between the convex portion 45 of the wheel gear 18 and the arm 16 is
Since it is located near the line connecting the shaft 27 and the shaft 100, the reaction force 174 does not generate a drag effective to prevent the engagement from becoming shallow. However, the effect of the aforementioned component force 175 prevents the engagement from becoming shallow.

FIG. 44 and FIG. 45 show the direction of
6 is shown. The driving force 172 applied from the worm gear 27 generates a component force 177 that is directed upward on the paper. The upward component force reduces the meshing relationship between the worm gear and the wheel gear, but the reaction force 174 acting on the convex portion 45 as described above is effective in preventing the meshing from becoming shallow. Since no drag is generated, for example, the tooth tips of the resin wheel gears are lost, or the tooth tips of the gears ride up and become immobile.

As in the embodiment shown in FIG. 40 and FIG.
When the contact position between the convex portion 45 of the wheel gear 18 and the arm 16 is located near the line connecting the worm gear 27 and the shaft 100, the stop position of the gear is engaged by the component force generated by the driving force from the worm gear. By determining the tooth streak in such a direction that does not become shallow, the freedom of arrangement of the operating lever, the wheel gear, the worm gear, and the like can be obtained, and a compact door lock power actuator can be realized.

FIG. 46 shows an embodiment in which a cam surface is provided between the convex portion 45 of the wheel gear 18 and the arm 16, the lever ratio is improved, and the output of the output shaft 10 is increased.

In FIG. 17, the operational relationship between the convex portion 45 and the arm 16 has been described.
In order to improve the lever ratio, the contact point between the protrusion 45 of the wheel gear 18 and the arm 16 is located as close to the rotation center side of the wheel gear 18 as possible, and the contact point between the protrusion 45 of the arm 16 and the contact point Is preferably located as far away from the center of rotation of the lever 17 as possible. Wheel gear idled between gaps 46
The tip 225 with the taper of the 18 convex part 45 and the R attached to the tip
And a substantially C-shaped cam surface 22 extending toward the tip of the arm 16
6 contacts. The substantially C-shaped cam surface 226 of the arm 16 is effective in arranging the contact point of the tip portion 25 of the convex portion 45 as far as possible from the rotation center of the lever 17.

The cam surface 226 having a substantially C-shape is changed from the middle to a cam surface 227 that is narrower toward the tip. The cam surface 227 and the tip portion 225 start contacting at a substantially intermediate position of the operation of the lever 17, and the cam surface 2 formed gradually and continuously with the tip portion 225.
At the stop position where the arm 17 is stopped by the stopper 39, the cam surface 228 is completely in contact with the cam surface 227 of the arm 16.

In this way, at the stop position where a large impact load including the motor rotational inertia is applied, by contacting the cam surface 228 having a large surface, wear and deformation of the tip 225 are prevented, and stable performance is obtained for a long period of time. be able to.

Next, there is a gap 230 between the extension 229 extending toward the rotation center of the lever 17 of the arm 16 and the tip 225.
Are set, and are arranged so as to interfere with the extension portion 229 and the tip portion 225 on the rotation trajectory of the lever 17.

At the time of manual locking and unlocking operation, the arm 16 of the lever 17 runs idle between the distal ends 225 of the convex portions 45.

In the locked and unlocked positions, the motor is driven in a state where the stopper 39 is elastically deformed by being further loaded in the operating direction, the gap 230 is eliminated, and the arm 16 is within the rotation locus of the wheel gear tip 225. When the switch is turned on, the tip 225 and the arm 16 interfere with each other, do not operate normally, and damage or break the respective contact surfaces.

In the embodiment, since the extension portion 229 is provided on the arm 16, even if an overload is applied, the arm 16 does not enter the operating locus of the wheel gear, and normal operation by operating the switch can be ensured.

In addition, by setting the gap 230, the arm and the convex portion do not interfere with each other in a normal manual operation, so that there is no hit between the resins and a good operation feeling can be obtained.

A switch for detecting that the key has been locked or unlocked by operating the key will be described in detail. FIG. 22, FIG. 47, FIG.
Refer to FIG. 23, FIG. 48, and FIG. Detection switch 205
The main body 207 is fixed to the sub-housing 2 ′ by a screw 206 or the like, and is rotatably supported by the main body 207.
208 is inserted into the hole 209 of the key operation lever 13 and includes a movable portion 210 that operates in conjunction with the rotation operation of the key operation lever 13, and internally has the same contact portion and conduction portion as shown in FIG. Detects locked and unlocked positions.

221 is a wire harness connected to the detection switch 205.

The sub-housing 2 'is provided with a cavity 212 for accommodating the aforementioned main body 207, and has a hole 213 into which the screw 206 is tightened.

The substantially U-shaped groove 214 is formed by the walls 215 and 216, serves as a passage for the wire harness 211, and continues to a passage 217 provided on the side wall. A clip 218 is locked to the wall 215, and the upper end piece 219 is
The opening 4 is closed to prevent the wire harness 211 from jumping out of the groove 214. FIG. 60 is a view as viewed from the arrow N in FIG.

The wire harness 211 is fixed to the housing by a clamp 186 as shown in FIG. 57 similarly to the embodiment shown in FIG.

In this manner, the wire harness 211 is firmly held on the upper surface of the sub-housing 2 'by the clip 218 and the clamp 186, and a sufficient clearance can be given to the glass elevating locus 114 in FIG. Required space can be reduced, and a compact door lock having a high degree of freedom in arrangement in a vehicle can be obtained.

If there is sufficient clearance between the door glass elevating locus 114 and the wiring harness 211 on the side of the housing, there is a hook 231 provided on the main housing 2 shown in FIGS. 58 and 59. By locking the wire harness 211, the harness can be prevented from freely floating from the surface of the sub-housing 2 ', and the number of parts and assembly can be reduced as compared with those using the clamp 186 shown in FIGS. Workability is low.

Refer to FIG. 47, FIG. 23, and FIG. Key operation lever
The rotation operation of 13 is transmitted from the protrusion 14 and the step 14 ′ to the protrusion 15 of the locking arm 9 to rotate the locking arm 9.

The switch 205 needs to be arranged closer to the door lock in order to ensure a sufficient clearance with respect to the glass lifting locus 114 in FIG.

As shown in FIG. 23, near the rotation center of the key operation lever 13 and the locking arm 9 and the switch 205, the projection 15 is bent toward the sub housing 2 ', and the projection 15 is A recess 220 is provided between the working range of the projection 15 to ensure a clearance between the housing 2 '.

With this arrangement, the switch 205 can be moved closer to the door lock.

In addition, a recess 221 is provided on the bottom surface of the movable portion 210 of the switch 205 to avoid interference between the locking arm 9 of the output shaft 10 and the caulking portion 222, so that the switch 205 can be further moved toward the housing.

FIG. 50 shows details of a fastening portion between the main body 207 and the sub housing 2 '.

A boss portion 223 is provided on the mounting surface side of the sub-housing 2 'of the main body portion 207, and the boss portion 223 provided on the sub-housing 2' is inserted to provide a hole 224 for determining the position of the switch 205. ing.

Thus, the switch 205 is formed by the boss 223 and the hole 224.
Is the one end 208 of the movable part 210 and the hole 209 of the key operation lever 13.
Are installed in the correct relationship, and lock and unlock are accurately detected.

Refer to FIG. 29 and FIG. 184 is motor 26, substrate 1
The wiring harness is connected to the conductive portion 22 and is fixed to the housing by a clamp 186 penetrating through a clamp hole 185 provided in both housings 2, 2 '. Therefore,
When assembling to a vehicle, pulling the connector (not shown) at the tip of the wire harness and connecting it to the mating connector, or holding the connector and hanging down the door lock body, this tensile load Since it is borne by the clamp 186 and does not extend to the portion housed in the housing, it does not damage the coupling portion with the motor or the coupling portion with the conductive portion of the board, and can prevent immovability due to disconnection. .

FIG. 52 shows an O-ring 119 inserted along the groove 118 in FIG. 24, a harness holding portion 198 through which a wire harness disposed in a conducting portion of the motor and the substrate passes, and an O-ring 119 inserted into the groove 118. A grip section 199 for improving workability of the camera is provided.

FIG. 53 shows details of the grip portion 199, in which a protrusion 200 is provided on the outer circumference, and the diameter 201 is set to be slightly larger than the width of the groove 118 described above. The groove 118 has a meandering shape with a small number of straight portions as shown in FIG. 24 in order to reduce the outer shape of the driving section. When the O-ring 119 is inserted and routed in the groove 118, the O-ring itself becomes linear. Due to the restoring force to return, it protruded from the groove, and the workability was extremely poor.

In the embodiment, by providing several grips 199 having an outer diameter shape larger than the groove width, it is possible to prevent the above-mentioned phenomenon of protruding from the groove, to greatly improve the insertion work, and to improve both the housings 2 and 2. ′, The seal performance is impaired, and water, dust, etc., do not enter the inside of the housing, and the function of the drive unit is not reduced.

FIG. 54 is an N view of FIG. 52, which has a hole 202 through which the wire harness passes.

FIG. 55 is a cross section taken along line PP of FIG. 54, and the inside of the hole 202 has a projection 20 having a diameter smaller than the outer diameter of the harness.
Three are provided.

FIG. 56 shows that the harness holding portions 19 are provided on both housings 2, 2 '.
8 shows a state in which both housings 2 and 2 'are mounted.
Are provided with convex portions 204 and 204 ', and a harness holding portion is provided.
198 is pressed.

Rainwater and dust ingress between the harness and hole 202
It is prevented by the convex portion 203 and between the harness holding portion 198 and the housings 2 and 2 'by the convex portions 204 and 204'.

Further, the convex portion 203 has a function of restricting the movement of the harness, and performs a displacement prevention when a load is applied to the tip of the harness.

(Effect) The present application solves the relationship between the reaction force acting on the convex portion of the wheel gear and the meshing reaction force in the direction of the tooth streak, so that there is no increase in cost, the thickness of the actuator portion is thin, and
Since the position of the motor is not limited, it is possible to arrange the motor in a manner similar to the space in the door, so that a compact actuator can be obtained.

[Brief description of the drawings]

FIG. 1 is a front view showing this embodiment, FIG. 2 is a partial front view showing a state in which an open lever operates a release lever, and FIGS. 3 and 4 are partial front views showing a swinging state of a locking mechanism. , FIGS. 5 and 6 are partial front views showing a keyless lock mechanism, FIGS. 7 and 8 are partial front views showing a self-cancelling mechanism, FIG. 9 is an exploded view of an actuator section, and FIG. FIG. 11 is a front view of a worm, FIG. 12 is an exploded perspective view of a mounting portion of an output shaft, FIG. 13 is a side view showing mounting of a turnover spring, and FIG. 14 is an operation lever. FIG. 15 is a graph showing the relationship between the wheel rotation angle and the motor reversing torque, FIG. 16 is a sectional view of the output shaft portion, FIG. 17 is a front view of the actuator section, and FIG. The illustration shows the side of the storage part of the door lock device Fig, 19 Fig. Is a side view of the door locking device, FIG. 20 is a partial sectional view showing the O- rings between the two housings, FIG. 21 is an enlarged partial front view of the switch unit,
FIG. 22 (a) is a front view of the door lock device, FIG. 22 (b)
Is a partial perspective view of the switch section, FIG. 23 is a side sectional view of the actuator section, FIG. 24 is a front view of the actuator section, and FIG.
FIG. 26 is a partial sectional view showing a screw fastening portion, FIG. 26 is another partial sectional view of a screw fastening portion, FIG. 27 is a sectional view showing a stored state of a stopper, and FIG. FIG. 29 is a rear view of the door lock device as viewed from the vehicle mounting surface side, FIG. 30 is a plan view showing a motor and worm gear shaft support structure, and FIG. 31 is an arrow DD in FIG. FIG. 32 is a cross-sectional view taken along the line EE in FIG. 20, and FIG.
FIG. 33 is a sectional view taken along the line FF in FIG. 20, and FIG.
FIG. 35 is a sectional view taken along the line GG in FIG. 20, FIG. 35 is a partial plan view showing engagement between the worm gear and the wheel gear, and FIG.
The figure is a partial plan view in which the pitch between the two gears is large, FIG. 37 is a partial plan view showing a state in which the worm gear is transversally displaced,
FIGS. 38 and 39 are front views showing the reaction force acting on each part,
FIG. 40 is a diagram showing the component force when viewed from the direction of arrow H in FIG. 38, FIG. 41 is a diagram showing the component force as viewed from the direction of arrow J in FIG. 38, and FIG. FIG. 43 shows the component force seen from the arrow K direction, FIG. 43 shows the component force seen from the arrow L direction in FIG. 39, and FIG. 44 shows the K direction in FIG. 39 when the teeth are reversed. FIG. 45 is a view from the L direction of FIG. 39 when the tooth streaks are reversed, FIG. 46 is a front view showing the relationship between the operating lever and the wheel, and FIG. 47 is a front view of the housing part. , FIG. 48 is a cross-sectional view showing a wire harness clip, FIG. 49 is a cross-sectional view showing a passage of a wire harness, FIG. 50 is a cross-sectional view of a mounting portion of a switch portion, and FIG. 51 is a cross-sectional view of a clamp portion of the wire harness. FIG. 52 is an overall view of the O-ring, and FIG.
52 is a sectional view taken along the line QQ in FIG. 52, FIG. 54 is a view as seen from an arrow N in FIG. 52, FIG. 55 is a view as seen from an arrow P in FIG. 54, and FIG. And FIG. 57 is a sectional view of a clamp portion of the wire harness, FIG. 58 is a perspective view showing a hook of the housing, FIG. 59 is a side view showing the clamp portion, and FIG.
The figure is a view as seen from the arrow N in FIG. In the figure: 1 ... door lock device, 2, 2 '... housing,
3 ... Release lever, 5 ... Open lever, 8 ...
Locking button, 9 Locking arm, 10 Pin, 13 Key operating lever, 15 Projection, 17 Actuating lever, 24 Return spring, 26 Motor, 27
... worm gear, 34 ... bearing part, 36 ... turnover switch, 39 ... stopper, 159 ... elastic material, 166 ... backlash, 225 ... tip part, 226, 227, 228 ... cam surface.

Claims (1)

(57) [Claims] A worm rotatably driven by a motor, a worm gear meshing with the worm, a convex portion provided on a wheel gear, and an operating lever having an arm portion abutting the convex portion, and a stopper at a lock and unlock position. When the movement of the operating lever is restricted and the arm of the wheel gear and the arm come into contact near the line connecting the wheel gear rotation center and the worm, the elastic deformation of the wheel gear caused by the meshing reaction force causes the axial deformation of the wheel gear. The tooth streak is determined so as to be displaced toward the root side, and the displacement of the wheel gear at the other end in the axial direction is prevented by the reaction force acting on the convex part of the wheel gear, and the normal meshing state A door lock device characterized by maintaining the following.