JPH0230870A - Door locker - Google Patents

Abstract

PURPOSE:To prevent deformation and damage to operating lever, etc., by a method in which the projection of a wheel gear is provided with a contact point to be touched initially by the arm of the operating lever and a contact point to be finally touched by the arm. CONSTITUTION:When an electric current is supplied to an electric motor 26, a wheel gear 18 is turned through a worm 27, and one end 19 of a projection 45 comes into contact with the arm 16 of an operating lever 17. The lever 17 and a pin 100 are turned to turn a locking arm to locking position. When the gear 18 is turned reversely, the other end of the projection 45 comes into contact with the arm 16 to turn the locking arm to unlocking position.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a door lock device that efficiently transmits rotational torque of a wheel gear to an operating lever.

(Prior Art) A door lock device has a link mechanism for operating a door lock mechanism, and the link mechanism can be operated by an actuator including an electric motor. This actuator transmits the rotational torque of the electric motor to the wheel gear via the worm gear, and rotates the operating lever while bringing the protrusion of the wheel gear into contact with the arm of the operating lever to operate the link mechanism. .

(Problem to be solved by the present invention) When locking and unlocking operations are performed manually,
The arm portion of the operating lever runs idle between the convex portions of the wheel gear. If the manual operation is excessive, the elastic deformation of the stopper causes the arm portion to enter the rotation locus of the convex portion of the wheel gear, blocking the rotation of the wheel gear driven by the motor, and preventing normal operation. In addition, a load is applied to the output shaft and the lever in a direction other than the direction of rotation, causing deformation or damage to the housing bearing portion or a portion of the lever.

Therefore, it is an object of the present invention to solve the above-mentioned problems of the prior art.

(Means for Solving the Problems) In order to solve the above-mentioned problems, the present invention basically provides a contact point where the tip of the convex part of the wheel gear initially contacts the arm part of the actuating lever, and a contact point where the tip of the convex part of the wheel gear initially contacts the arm part. A configuration including a contact surface that makes final contact is adopted.

More specifically, in the present invention, the locking and unlocking actiniator is provided with a convex part provided on a wheel gear that is rotated by the drive of a motor, and an arm part that comes into contact with the convex part. The convex portion has an arm portion on the rotation center side of the wheel gear, an initial contact point, and a stopper that restricts the operation of the lever. It has an arm portion and a contact surface that makes final contact.

The initial contact portion of the arm portion with the convex portion of the wheel gear is as follows:
It has a roughly V-shaped cam surface that widens toward the tip.
The cam surface, which becomes the final contact point from the contact point with the wheel gear protrusion at approximately the middle position of the lever's operating range, is formed to be narrower toward the tip, which improves the output by increasing the lever ratio at the time of initial contact. When the movement of the lever is stopped by the stopper and the final contact occurs, the surfaces contact each other to prevent wear, damage, etc.

(Function) When the tip of the convex part of the wheel gear initially makes contact, the lever ratio is small, but when it finally makes contact, the lever ratio increases (the fourth
(See Fig. 6), since both surfaces are in contact with each other, high torque is smoothly transmitted from the convex portion to the arm portion.

(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 an abbreviated release lever 3 pivotally supported by a main housing 2 made of synthetic resin. This release lever 3 is rotatable around a fulcrum 26 at its center.

This fulcrum 26 is also the center of rotation of a pawl of a door lock actuating unit including a ratchet and pawl (not shown), and the release lever 3 is interlocked with the pawl via a pin 27. When the door is closed, the above-mentioned pawl engages with a latch provided on the door lock operating portion that engages with a striker attached to the vehicle (not shown). The position of the release lever 3 shown in Figure 1 is a state in which the aforementioned latch of the door lock and the pawl are engaged, and by rotating this lever 3 counterclockwise, the pawl rotates the ratchet and the aforementioned latch and pawl are engaged. A latch release state is obtained in which the mesh is disengaged, and the door can be opened. When the outside handle is operated, a force is applied in the direction indicated by 29, and the rod 4 rotates the lever 30, which is pivotally supported on the main housing 2, counterclockwise about the fulcrum 31. Also, when the inside handle is operated, a force is applied in the direction shown by 28, and lever 3
0 in the counterclockwise direction around the fulcrum 31.

The counterclockwise rotation of the lever 300 pushes down the oven lever 5 pivotally attached to one end of the lever 30. The downward movement of the oven lever 5 is caused by the protruding piece 6 at the center of the oven lever 5 pushing the first part 7 of the release lever 3 and rotating the release lever 3 counterclockwise around the fulcrum 31. to enable the door lock to be in the latch release state and open the door (see Figure 2).

To prevent the door from being opened inadvertently while the vehicle is running,
To lock the door, generally use locking button 8
The door is locked by pressing and rotating the locking arm 9 clockwise. A portion of the locking arm 9 is connected to the lower part of the oven lever 5 via a long length. Locking arm 9 is the first
When in the position shown, the lowering of the oven lever 5 allows its protrusion 6 to come into contact with the end 7 of the release lever 3.

However, when the locking button 8 is pressed and the locking arm 9 is rotated clockwise together with the pin 10, the oven lever 5 moves in the direction of arrow C, and the protrusion 6 is moved to the end 7 of the release lever 3. (See Figure 3). As a result, if you operate the handle, you can use the oven lever. (See Figure 4).

The keyless lock mechanism will be explained. With the door open, press the locking button 8, rotate the locking arm 9 clockwise, and push the protrusion 6 into the release lever 3.
The end portion 7 of the When the outside or inside handle is operated, the open lever 5 is pushed down, resulting in the state shown in FIG. 5. When the door is closed in this state, the release lever 3 is rotated counterclockwise, but the step 11 of the open lever 5 and the protrusion 12 of the release lever 3
The release lever 3 is free to rotate counterclockwise, and the door is kept locked. (
(See Figure 6). After the door is closed, the release lever 3 is brought into the state shown in FIG. 5 by the spring of the door lock operating section, and returns to the state shown in FIG. 3 when the handle is no longer operated.

Next, the self-cancelling mechanism will be described. With the door open, press the locking button 8, rotate the locking arm 9 clockwise, and rotate the open lever 5 in the direction C shown in Figure 1 to return to the state shown in Figure 7. 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 section (not shown). This movement causes the protruding piece 12 of the release lever 3 to come into contact with the stepped portion 11 of the open lever 5, causing the open lever 5 to
Rotate it clockwise as shown in FIG. As a result,
The locking button 8 is returned to its original position and the locking arm 9 rotates counterclockwise around the pin 10 via the length of the open lever 5. That is, the state returns to the state shown in FIG. 1, so when the handle is operated to open the door, the protrusion 6 of the open lever 5 pushes down the end 7 of the release lever 3, and the lever that enables the door to open is pressed down. Set to locked state.

Key operations will be described with reference to FIG.

A key operation lever 13 is rotatably supported by the housing 2', and its protrusion 14 is arranged in parallel with the protrusion 15 of the locking arm 9. This lever 13 is connected at one end to a key cylinder via a loft. When the key is operated in the locking direction, the key operation lever 13 rotates clockwise from position A to position B, and the locking arm 9 is rotated clockwise due to the contact between the protrusions 14 and 15. When the locked state of the door lock is secured and the key operation is stopped, the key operation lever 13 returns from position B to position A by the action of a spring attached to the key cylinder side. That is, the locking button 8 is pressed down, in other words, the open lever 5
The protruding piece 6 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. When the key is rotated in the unlocking direction, the stepped portion 14' pushes against the protrusion 15, and the locking arm 9 is rotated counterclockwise to the unlocked state shown in FIG. In the state shown in FIG. 1, even if the key operation lever 13 is rotated to the position B' using the key, the step 14' will only approach the protrusion 15 and the locking arm 9 will rotate. There isn't.

In addition to the above-mentioned manual operation, 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 obtain a state in which locking and afro-locking are possible. Things will be done. See FIG. 9. An operating lever 17 having an arm portion 16 is fixed to the pin IO. Both ends 19 and 20 of the pair of raised protrusions of the wheel gear 18 rotatably supported by the housing are opposed to the downward arm 16 at the tip of the operating lever 17.

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, this groove 21 is partially narrowed by opposing wall surfaces 22 and 23. Put the coil spring 24 into the groove 21, and attach the end of the coil spring 24 to the wall surface 2.
2.Put it in contact with 23's shoulder. Furthermore, wheel gear 18
A projecting piece 25 protruding from the lower surface of is positioned between the wall surfaces 22 and 23. As a result, for example, when the wheel gear 18 rotates clockwise as seen in FIG. 10, the protrusion 25 compresses the spring 24 while pushing the right end of the spring 24. At this time, the left end of the spring 24 abuts against the shoulder of the wall surface 22.23, allowing the spring 24 to be compressed. This rotation of the wheel gear 18 causes the end 19 of the convex portion 45 to come into contact with the arm portion 16, causing the operating lever 17 and pin 10 to rotate, allowing the locking arm 9 to move from position A to position B. Make it. When the wheel gear 18 is rotated in the opposite direction, the protrusion 25 compresses the spring 24 counterclockwise while bringing the right end of the spring 24 into contact with the shoulder of the wall surface 22.23, and the end 20 causes the actuation lever 17 to and rotate the pin 10 to move the locking arm 9 from 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.

The wheel gear 18 rotatably supported by the housing meshes with a worm gear 27 directly connected to an electric motor 26, and by controlling the power supply to the motor 26, the wheel gear 18 is rotated.
The direction of rotation is controlled.

Generally, when the advance angle To of the worm gear becomes larger than the friction angle φ, rotational torque can be transmitted from the wheel gear 18 to the worm gear 27. Therefore, in this example, μ
(Friction coefficient) Utilizing the relationship of =tanφ, the advance angle is set to be equal to or greater than the friction angle (φ=8.53°). That is, the worm gear 27 made of phosphor bronze and the wheel gear 1 made of resin.
8 friction coefficient μ = 0.1 to 0.15, friction angle φ = 5.7
1° to 8.53°, and the friction angle is set to 8.53° or more to enable rotation of the worm gear 27 from the wheel gear 18. Such a lead angle (γ) of the worm gear 27.

) is selected such that, even if the wheel gear 18 is rotated by the door lock operation by the driver using the electric motor 16, the wheel gear 18 can be returned to the original position by the spring 24 immediately after the operation, and then allows manual operation. In other words, it enables manual and then electric operation, or electric and then manual operation. In addition, since the actuating lever 17 and the wheel gear 18 are completely separated during manual operation, the arm portion 16 only runs idly between the pair of ends 19 and 20 of the convex portion 45, and the motor portion is turned. It is easy to operate without any problems, and has a good operating feel.

As shown in FIG. 12, the motor 26 inside the sub-housing 2'
The pin 10 fixed to the actuating lever 17, which is actuated by the pin 10, has a working part and a square part at its tip, and is inserted into the stepped hole 32 of the housing 2'. The outer peripheral surface of the stepped hole 32 serves as a bearing portion 34 that receives the hole 33 of the key operation lever 13 on its outer peripheral surface. The square portion 9 of the pin 10 that protrudes from the bearing portion 34 when the pin 1O is inserted into the bearing portion 34 is seated on the top surface of the bearing portion 340. Since the bearing part 34 for the key operation lever 13 is formed integrally with the housing 2, a separate bearing is not required, and the mounting part of the locking arm 9 does not protrude outward.

Each end of the turnover spring 36 that holds the locking arm 9 in the locked and unlocked positions is
As shown in the figure, it is engaged with a recess 37 of the housing 2 near the bearing part 34 and a hole 38 of the locking arm 9 which extends into the recess 37 and is opposite to it. In this example, since the pin 10 is directly connected to the locking arm 9, the rotational force from the motor is efficiently transmitted to the turnover spring, so that the operating force can be small. This means that motor 2
6, making it possible to downsize the entire device.

As already understood from the explanation of FIG. 1, the fulcrum 26, which is the center of rotation of the release lever 3, also serves as the center of rotation of the pawl of the door lock operating section (not shown), and the pin 27, which can freely come into contact with the pawl, supports the pawl. The door lock operating section is thus housed within the housing 2, as shown in FIG. The various levers and arms described above are arranged on the outer surface of the housing 2. On the other hand, pin 1 serves as the output shaft including the motor 26, etc.
The actuator for rotating the door lock is housed in the extension of the housing 2 for the door lock actuator. Furthermore, compared to a system in which the motor 26 and the wheel gear 18 are arranged in parallel and the driving force is transmitted to the output shaft 10 via a speed reduction mechanism such as a spur gear, the electric motor 26 rotates the operating lever 17. The locking arm 9 is moved to the locked position (B) and unlocked position (B') shown in FIG.
A stopper 39 for stopping the operating lever 17 is arranged at these positions ffi (B, B'). The function of this stopper 39 will be explained with reference to FIG. 14. Although FIG. 14 shows only one stopper 39, the function of the other stopper is the same, so the drawing and explanation thereof will be omitted.

The operation of the electric motor 26 causes the wheel gear 18 to rotate via the worm 27, and the end 19 of the convex portion 45 to rotate the operating lever 17 together with the pin IO. At this time, the return spring 24 is bent and stores energy for returning the wheel gear 18 to the neutral position. In this example, when the actuating lever 17 reaches the normal stop position 40, the actuating lever 17 and the stopper 39 come into contact and attempt to prevent the movement of the actuating lever 17, but due to the rotational inertia of the motor, the stopper 39 The operating lever 17 moves to the overtravel position 41 while being elastically deformed.

That is, the stopper 39 is elastically deformed by the amount of overtravel. The stopper 39 is made of a solid or hollow body such as rubber or synthetic resin that allows such elastic deformation. It functions to push back the operating lever 17 to the normal lock/unlock position together with the spring 24. The auxiliary force from this stopper 39 is
Correspondingly, the biasing force of the spring 24 and the output of the electric motor 26 can be reduced. Incidentally, the relationship between the wheel gear 18 and the motor reverse rotation torque is shown in FIG.

Although the relationship between the pin 10 and the housing 2 is shown in FIG. 12, it will be explained in more detail using FIG. 16.

The pin 10, which is an output shaft fixed to the operating lever 17, has a stepped structure consisting of a large shaft diameter portion 40 and a small shaft diameter portion 41. On the other hand, the hole 32 of the housing 2' has a large opening 42 for receiving the large shaft diameter part 40 and a small shaft diameter part 41.
It consists of a small opening 43 that receives the opening. Housing 2'
The locking arm 9 is fixed to the smaller shaft diameter portion 41 that protrudes further, and the key operation lever 13 is rotatably supported by the bearing portion 34 of the housing 2'.

When installing the pin 10 into the hole 32 of the housing 2', fit the O-ring 44 into the small shaft diameter part 41 of the pin 10, and insert it from the inside of the housing 2' so that the small shaft diameter part 41 protrudes from the housing 2'. Insert the output shaft 10 into the hole 32. To insert the output shaft lO into the hole 32, use the O-ring 44.
The stepped portion of the hole 32 is opposed to the stepped portion of the pin 10 via the hole 32.

In this way, movement of the pin 10 relative to the housing 2' can be restricted. This is useful to ensure correct movement of the actuation lever 17.

Further, since the O-ring 44 can be attached to the pin 10 by simply attaching it to the hole 32 of the housing 2', the assembly work is extremely easy.

In the illustrated example, in order to rotate the operating lever 17, the first
As shown in FIG. 6.17, the wheel 18 is provided with a semicircular arc-shaped rising portion 45, but instead of this, a pair of pins may be installed on the wheel 18. End portion 19 of convex portion 45.
20 can come into contact with the arm 16 of the operating lever 17.

When the electric motor 26 is energized, the wheel 18 rotates via the worm 27. Depending on the rotation direction of the wheel gear 18, one end of the convex portion 45 comes into contact with the arm 16, compressing the return spring 24 and moving the operating lever 17 to the lock or unlock position, so that the pin 10 serving as the output shaft is moved. Move the link mechanism. When the actuating lever 17 is in the lock or unlock position and the power to the motor 26 is turned off, the releasing force of the compressed return spring 24 causes the wheel 18, the worm 27 and the motor 26 to rotate in the opposite direction, and the wheel 18 is placed in the neutral position. Return to position. When the wheel 18 returns to the neutral position, a gap 46 is left between the end of the convex portion 45 and the arm 16, as shown in FIG. This gap 46 allows the rotation speed of the electric motor 26 to be immediately rated when the electric motor 26 is energized. Increases static friction in locking mechanisms, etc. That is, when the convex portion 45 comes into contact with the arm 16 of the operating lever 17, the rotational inertia energy of the motor can be transmitted to the arm 16, thereby making it possible to downsize the motor.

Having described the door lock device 1, the mounting portion of the door lock device 1 will now be described with reference to FIG. 18. The vehicle has a center pillar 49 between the front door 47 and the rear door 48;
A hinge 50 and a striker 51 for the rear door 48 are fixed to. The striker 51 can be freely engaged with and disengaged from a ratchet (not shown) of the door lock device 1 when the front door 47 is opened or closed. On the other hand, when the windshield 52 of the front door 47 moves up and down, it follows a trajectory 5 along the center pillar 49.
Move along 3. Therefore, the door lock device 1 fixed to the front door 47 side avoids the trajectory 53 of the windshield 52, and the door lock device 1
It is necessary to prevent interference with In order to avoid such interference, a concave portion 54 is formed on the front edge of the center pillar 49 and an overhang 55 is formed on the rear edge of the front door 47, and the door is inserted into the overhang 55. Lock device 1
to be stored. That is, the door lock device 1
It is necessary to have an external shape that fits within the limited space of 5. Note that the shapes of the projecting portion 55 and the concave portion 54 are designed so as 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 shown at 113.

As is clear from FIG. 16, in this example, the lower part of the main housing 2 is extended and the electric actuator is arranged in this extension, so the actuator is supported by the sub-housing 2', and this sub-housing 2' is used as the main housing. It is fixed to the housing 2. The main housing 2, which is housed in the above-mentioned limited space overhang 55, has a lower portion extending forward.

See FIG. 19. A mating surface 115 of the sub-housing 2' that is mated to the main housing 2 whose lower portion 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 improve the sealing performance therebetween. In order to further improve the sealing performance of both housings 2.2', that is, to prevent the mating surfaces 115 of both housings 2.2' from shifting, a pair of hooks 117 are provided at the bottom of the sub-housing 2', as shown in FIG. are provided, and this pair of hooks 117 are brought into contact with the lower end surface of the main housing 2. The contact of the hook 117 with the lower end surface of the main housing 2 (see FIG. 20) prevents displacement when the two housings 2.2' are fastened, improving sealing performance, and furthermore, the contact between the pin 10, which is the output shaft, and the The pin receiver of the housing 2 prevents misalignment with the hole.

Referring again to FIG. A substantially U-shaped groove 118 is arranged along the inner edge of the main housing 2, a rubber O-ring 119 is inserted into this groove 118, and the O-ring 119 is secured by the mating surface 115 of the sub-housing 2'. Flex it to ensure sealing pressure. The inner edge of the main housing 2 has a wall 120 extending upward, and even if rainwater or dust passes through the O-ring 119, this wall 120 prevents the rainwater or dust from entering into the housing 2. . This wall 120 is
It is also effective to improve sealing performance when the mating surfaces of both housings 2.2' are bonded or welded.

As mentioned above, the shape of the housing is approximately dogleg-shaped with the lower part protruding toward the front of the vehicle, so that the operating lever 17 is attached to the shaft portion 121 fixed to the output shaft 10, as shown in FIG.
An arm portion 124 extends to the left in the drawing and holds a contact 123 that detects the locked/unlocked state in cooperation with a board 122 fixed to the housing 2. The arm portion 124 is arranged to avoid interference with the lower shape of the housing. A stepped portion 125 is provided which connects the arm portion 16.

A ring-shaped convex portion 126 is formed on the side of the shaft portion 121 that contacts the bearing surface of the housing 2', which facilitates dimension control in the thrust direction, reduces the contact surface with the housing 2', and reduces rotational resistance. Grease retention 12
7 is formed.

Further, the arm portion 16 is slidably supported by a convex portion 128 provided on the housing 2, thereby preventing an increase in rotational resistance due to full rotation of the arm portion and the housing.

The aforementioned contact 123 is connected to the arm portion 124 of the operating lever 17.
It consists of a fixing part that is attached to the protrusion 129, 129' and a contact part 130, 130' that slides on the base plate 122, and the fixing part has a locking part that prevents the arm from being removed from the protrusion. 131 is equipped.

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

The board 122 is made of an insulator such as epoxy resin,
Conductive parts 131 and 131' made of copper or the like are arranged in the passage parts of the aforementioned contact parts 130 and 130'.

In the embodiment, the conductive portions 131.131' are the contact portions 130.131'.
130' and the detection circuit is open, it is set as an unlocked state, and when it is closed, it is set as a locked state.

In this way, since the switch part is arranged on the operating lever 17 that is directly connected to the locking lever 9 that switches between locking and unlocking, the degree of detection of one position is improved. The arrangement avoids overlapping the contactor 129 of the arm section 124 of the actuating lever 17 with the protrusion 129 that fixes the contact 123, so the board and the arm section can be brought as close together as possible, and the height of the drive section can be kept low. can.

Please refer to FIGS. 22 and 23. When a seal 189 made of rubber or the like is attached to the door panel 187 with a clip 188 and seals between the door and the body and is arranged to pass over the actuator part of the door lock, the tip 190 of the clip 188 described above Interference is a problem.

In this embodiment, attention is paid to the empty space created above the motor housing portion of the housing 2, and a recess 191 is provided as depressed as possible to ensure a gap between the recess 191 and the tip 190 of the clip 188.

In this way, the actuator part is shaped like a dogleg,
Furthermore, by providing a recess to avoid interference with the tip of the clip, it is possible to reduce the substantial space required between the door panel 113 and the door glass vertical path 114 shown in FIG. A compact door lock with a high degree of freedom can be obtained.

In the embodiment shown in FIG. 22, the housings 2 and 2' are fastened together by a screw L192.

As shown in FIG. 17, FIG. 24, and FIG.
A hole 193 larger than the outside diameter of No. 2 is provided in No. 1 housing 2.
Fastening hole 194 slightly smaller than the outer diameter of screw 192
It has.

Refer to FIG. 26. By fastening housings 2 and 2'
In order to prevent the relationship between the screws 192 and 192 from shifting, the diagonally arranged hole in the housing 2' is made into a hole 195 that is slightly smaller than the outer diameter of the screw 192. It takes a structure where the center matches.

In this way, with the centering structure that is inexpensive and does not take up space, the pin 10 that occurs due to misalignment between the housings 2 and 2'
The output loss at the zero bearing can be reduced, and the motor output can also be reduced, making it possible to downsize the motor and achieve smooth and quiet operation.

Please refer to FIGS. 17, 24, and 27.

In order to prevent the stopper 39 held by the stopper holding portion 196 of the housing 2 from coming out, the stopper 3 of the housing 2' is
A removal stop 197 is provided at a position opposite to 9.

In this way, by providing the pull-out stop 197, an impact load including the rotational inertia load of the motor is applied to the stopper 39 through the actuating lever at the locked and unlocked positions, causing elastic deformation and holding the stopper as described above. Even if the stopper 39 tries to pull out from the section 196, the pullout is prevented by the stopper 197, so that the stopper 39 can be guaranteed to be held even under repeated loads, and stable performance can be maintained over a long period of time.

Further, since the stopper part is housed between the housings 2 and 2', the performance of the stopper rubber is not deteriorated due to the adhesion of foreign matter such as rainwater and clumps, and the durability is excellent.

Air venting inside the housing will be described with reference to FIGS. 16 and 28. The lower end of the housing 2 (on the left side in the paper) is provided with an air hole 107 formed in cooperation with the housing 2'. This prevents rainwater, etc. adhering to the interior from being sucked into the interior.

The shape of the air hole 107 is similar to that of the wall 10 facing the opening 108.
9 is provided, the air hole is formed into a substantially U-shape by the wall 109 and the opposing wall 110, and the size of the hole is as follows.
The side walls 111 and 112 form a substantially rectangular shape.

Therefore, even if water droplets such as rainwater adhere to the vicinity of the opening 108 or there are lumps or the like, the two walls 109 and 110 prevent them from entering the housing 2.

Draining water from the housing will be explained with reference to FIGS. 16 and 29.

A space 179 formed between the housing 2 and the plate 178 of the door lock that abuts the door locker mounting surface 116 of the door panel houses a well-known engagement mechanism for keeping the door closed.

A groove 180 is provided at the bottom of the space 179 to drain water such as rainwater, and is formed between the groove 178 and the plate 178, and extends as far as possible below the plate 178. .

At the bottom of the groove 180, the bearing part 181 of the pin 10 is placed as close to the door panel 113 as possible, and the water passage 182
is formed, and the groove 180 is substantially terminated by a wall 183.

In this way, by providing the wall 183 that limits the groove 180, the thickness of the door lock actuator part in the longitudinal direction of the vehicle can be reduced, and a gap between the door glass and the ascending/descending path 114 can be secured, and the door rotor device can be moved closer to the door. It can be placed in the upper position to improve the strength of the upper part of the door against collisions, etc., or it can be placed at the rear of the door from the vertical path, increasing the door glass area and increasing the degree of freedom in design. can.

Referring again to FIG. 16, the area around the shaft 100 will be explained.

The wheel gear 18 is rotatably connected to a shaft 100 inserted into the housing 2', and its movement in the removal direction is restricted by a washer 101 caulked to the tip of the shaft 100.

A washer 102 is inserted between the wheel gear 18 and the housing 2' to reduce resistance during rotation and prevent the resins from coming into contact with each other.

A ring-shaped convex portion 103 is formed on the contact surface of the wheel gear 18 with the washer 101, which facilitates dimension control in the thrust direction, reduces the contact area with the washer 101, and reduces rotational resistance. A grease reservoir 104 is formed.

The portion of the shaft 100 that is inserted into the housing 2' has a structure that increases the strength against bending and rotation of the shaft 100 that occurs when the worm gear 27 and the wheel gear 18 engage with each other.
In addition, in order to improve the holding strength in the thrust direction, the other end 105 of the shaft 100 and the washer 1010 are protruded from the surface of the housing 2' to the outside when the washer 1010 is caulked. A flange portion 106 is provided to lengthen the path when pouring water and prevent rainwater from entering.

FIG. 17 is a view from inside the housing 2',
The positional relationship between the pin 10, the operating lever 17, the wheel gear 18, the motor 26, and the worm gear 27 is shown. As is clear from FIG. 16, the pin 10 is supported by the bearing 34, and the wheel gear 18 is supported by the inserted shaft. 100, and the worm gear 27 and motor 26 are supported by supports 132, 133, 134 provided in the housing 2'.
The rotational movement of the motor itself is supported by the wall 1
35.136.

In this way, the positional relationship of the drive transmission system, especially the wheel gear 1
Since the meshing relationship between the worm gear 27 and the worm gear 27 is determined only by the sub housing 2', manufacturing errors such as gear pitch distance can be minimized, smooth power transmission is possible, and the motor outlet This will lead to a shift towards public affairs, which will reduce losses.

The motor support structure will be explained in detail in FIG. 30.

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 claws 139.

The motor shaft 140 has a bearing 141 fixed to the bearing part 137' of the case 137 by press fitting or the like, and a bearing part 1 of the case 138.
It is rotatably supported by a bearing 142 fixed to 38' by press fitting or the like.

The motor shaft 140 includes a commutator section 143 that receives electricity from the outside and a core 145 that holds a winding 144.
is fixed.

Further, in order to prevent interference between the winding 144 and the case 137, a collar 146 is disposed between the core 145 and the winding 144.

The Mazda net 14g is fixed to the case 137.

One end 147 of the motor shaft is machined into a spherical shape, and is supported by a metal thrust plate 149 disposed between it and the resin case 138.

This thrust plate 149 is connected to the other end 150 of the motor shaft.
It resists the load when the worm gear 27 is press-fitted into the knurl 151 provided in the housing, and prevents the resin case 138 from cracking. It also resists the thrust load generated during locking and unlocking operations, and improves durability. It is effective for

The bearing of the case 137 is the support part 13 that supports the part 137'.
3 and the support part 1 that supports the bearing part 138' of the case 138.
32 determines the thrust direction position of the motor and its positional relationship with the shaft 100 that pivotally supports the wheel gear 18.

Next, a description will be given of the support portion 134 that supports the shaft portion 152 of the worm gear 27 whose tip is machined into a spherical shape.

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

In addition, when a load is applied to the motor shaft 140 in the direction of entering the motor case side, and when one end 147 of the motor shaft contacts the thrust plate 149 and rotates, the rotational resistance is small because of the contact with the spherical surface, and the motor shaft rotates with a light torque. can do.

Conversely, if a load is applied in the direction of pulling out the motor shaft, the end face of the collar 146 and the end face of the bearing 141 come into contact, resulting in large rotational resistance and a large torque being required to rotate the motor shaft.

As shown in the example, in worm meshing, a load is applied in either the forward or reverse direction to push in or pull out the shaft, and the motor output needs to be large enough to account for the large rotational resistance mentioned above. Become.

Furthermore, if the motor is de-energized after being driven, the wheel gear 18 is driven by the return spring 24, and the worm gear 27 is rotated while returning to the neutral position. , the output of the return spring must also be increased, and the output of the motor must be increased accordingly. In this way, in order to prevent contact between the collar 146 and the bearing 141, which would cause various output losses, the shaft portion 152 of the worm gear 27 has a spherical tip.
and the support part 134 to absorb manufacturing errors between the motor shaft length 154 and the length 155 to the surface of the thrust load bearing of the support part 134, and to reduce the gap between the collar 146 and the end face of the bearing 141. Gap smaller than 153 Gap 156
is set.

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

The manufacturing error between the support parts 132 and 133 is
The direction is set in such a direction that there is a gap with the motor case to compensate for the amount that cannot be absorbed by elastic deformation of the case 138, and when the motor is assembled, the case 138 and the support part 132 are brought into contact with each other.

In addition, in the radial direction of the shaft portion 152 of the worm gear 27, a small gap is set between the supporting portion 134 and the operating lever, for example, when the actuating lever is stopped at the lock or unlock position, and the meshing reaction force with the wheel gear 18 causes a pitch. They will come into contact when the distance between them is about to increase.

When the power to the motor is cut off and the return spring 24 drives the wheel gear 18 and rotates the worm gear 27 to return to the neutral position, the support part 134 and the shaft part 15
2, since the contact is released, there is no loss of return spring force in this part, and therefore the return spring force can be reduced, and the motor can be made smaller. Further, since the support parts 132 and 133 determine the normal motor shaft, manufacturing errors can be easily absorbed, and an inexpensive housing can be obtained.

Next, the housing 2 is provided with the following support parts. That is, as shown in FIG. 31, the tip 1 of the worm gear
A support portion 157 is provided that comes into contact when the portion 52 is displaced.

As shown in FIG. 32, the bearing portion 13 of the motor case 137
A support portion 158 is provided to support 7'.

As shown in FIG. 33, an elastic body 159 such as a sponge is arranged in a bent manner on the housing 2 side of the motor case 137 supported by the housing 2'. If the dimension 160 between the support parts 132 and 133 is made large and a gap is created between the support parts 132 and 133 and the motor case, the opening/closing of the door, vibration during driving, or motor drive This prevents the motor case from moving due to worm engagement reaction force, etc., and causing abnormal noise.

As shown in FIG. 34, the bearing portion 138 of the motor case 138
A support portion 161 is provided to support .

Next, the meshing between the worm gear 27 fixed to the motor shaft 140 and the wheel gear 18 that meshes with this gear will be explained.

FIG. 35 shows a standard meshing state between the worm gear 27 and the wheel gear 18. 162 is the tooth of the wheel gear, 1
63 indicates the teeth of the worm gear, and 164 indicates the backlash at standard time. The shape of the wheel gear 18 is 16.1.
As shown in Figure 7, it has a complicated shape and is therefore made of resin. For products with such complex shapes and indeterminate wall thickness, distortion of the external shape due to molding is unavoidable, and if the face width increases, backlash will decrease and smooth tooth meshing operation will not be possible, and sinks may occur. If this occurs, a load will be applied to the tooth tips, resulting in a decrease in strength.

Generally, in order to increase backlash, a method of setting the pitch distance larger than the standard value, as shown in Fig. 36, is used, but reduction gears using small gears, such as module 0.6 (tooth depth 1.35 mm), are used. In this case, the pitch distance can only be increased by a small amount, and the required amount of backlash cannot be obtained. In addition, more load is applied to the tips of the teeth, and especially in levers that drive levers that come into contact with a fixed object and are restricted in operation after a predetermined operation, the motor rotation will suddenly stop when the stove is used. An impact load containing rotational inertia energy acts on the teeth, resulting in damage to the teeth themselves.

In the present embodiment shown in FIG. 37, the tooth profile and pitch distance of the resin wheel gear 18 are standard, and the teeth of the phosphor bronze worm gear 27, which has relatively sufficient strength, are transposed sideways to prevent backlash. increase. Reference numeral 165 indicates a worm gear tooth whose tooth width has become smaller due to lateral dislocation, and 166 indicates backlash that has increased due to lateral dislocation. Like this,
Since the distance between the pitches is standard, contact at the tips of the teeth can be prevented, there is no loss in strength, and strain on the teeth of the wheel gear can be absorbed.

Next, the relationship between the tooth line direction and the actuation lever will be explained in detail.

FIG. 38 shows the protrusion 45 of the wheel gear 18 and the actuating lever 1 that are engaged with the worm gear 27 due to the drive of the motor.
7 comes into contact with the arm 16, and the lever 17 comes into contact with the stopper 39.
The state shown is that it has moved to the unlocked position where it comes into contact with. Third
FIG. 9 similarly shows a state in which it has been moved to the lock position.

In FIG. 38, an arrow 167 indicates the driving force applied from the worm gear 27 to the wheel gear 18.

Arrow 168 indicates a reaction force from the stopper 39 to the actuation lever 17, and arrow 169 indicates a reaction force from the arm 16 to the end of the convex portion 45. FIG. 40 is a view from H in FIG. 38, and the wheel gear 18 is provided with teeth 170 facing upward to the right in the paper.

The driving force 167 given by the worm gear 27 generates a component force 171 directed upward in the plane of the paper due to the inclination of the teeth 170 in the case of a tooth line as shown. FIG. 41 shows J Motherland in FIG. 38, and the aforementioned component force 171 causes elastic deformation of the resin wheel gear in the direction of shallower engagement with the worm gear, counterclockwise in the plane of the paper, and the insertion of the shaft 100. However, the reaction force 169 acting on the protrusion 45 that generates a counterforce in the clockwise direction in the drawing prevents the meshing between the wheel gear and the worm gear from becoming shallow.

In FIG. 39, 172 indicates the driving force given to the wheel gear 18 by the worm gear 27, 173 indicates the reaction force from the stopper 39 to the actuating lever 17, and 174 indicates the arm 1.
6 shows the reaction force to the convex portion 45.

Figure 42 shows the motherland in Figure 39, and the worm gear 2.
The driving force 172 given by 7 generates a component force 175 directed downward in the plane of the paper.

FIG. 43 is an L view of FIG. 39, and the aforementioned component force 175
The wheel gear or the insert portion of the shaft 100 is elastically deformed in the direction of deeper engagement with the worm gear, that is, in the clockwise direction in the drawing.

When the actuating lever 17 is stopped by the stopper 39, the contact point between the protrusion 45 of the wheel gear 18 and the arm 16 is located near the line connecting the worm gear 27 and the shaft 100, so the reaction force 174 causes the engagement to occur. No effective drag is generated to prevent shallowing. However, due to the action of the component force 175 described above, shallow engagement is prevented.

Figures 44 and 45 show tooth 17 on the upper left side of the paper.
6 is shown. The driving force 172 provided by the worm gear 27 generates a component force 177 directed upward in the plane of the paper. This upward component force causes the meshing relationship between the worm gear and the wheel gear to become shallow, 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 tips of the teeth of a resin wheel gear may be lost, or the tips of the gears may run over each other and become immobile.

As in the embodiment shown in FIG.
If the stopper position is located near the line connecting the worm gear 27 and the shaft 100, and the contact point between the protrusion 45 of the wheel gear 18 and the arm 16 is located, the meshing will occur due to the component force generated by the driving force from the worm gear. By determining the tooth line in a direction that does not make it shallow, you can gain freedom in the arrangement of operating levers, wheel gears, worm gears, etc.
A compact power actiniator for a door lock can be realized.

FIG. 46 shows the protrusion 45 of the wheel gear 18 and the arm 16.
An embodiment is shown in which a cam surface is provided between the shaft and the lever to improve the lever ratio and increase the output of the output shaft 10.

The working relationship between the protrusion 45 and the arm 16 has been described in FIG. It is preferable that the contact point of the arm 16 with the convex portion 45 be located as far away from the rotation center of the lever 17 as possible. As the convex portion 45 of the wheel gear 18 that runs idle in the gap 460 tapers, the rounded tip 225 comes into contact with the substantially V-shaped cam surface 226 that widens toward the tip of the arm 16. . The substantially V-shaped cam surface 226 of the arm 16 is effective in arranging the contact point of the tip 25 of the convex portion 45 as far away from the center of rotation of the lever 17 as possible.

The substantially V-shaped cam surface 226 changes from the middle to a cam surface 227 that is formed thinner toward the tip. Cam surface 2
27 and the tip 225 begin to come into contact with each other at approximately the middle position of the operation of the lever 17, and gradually change to contact with the cam surface 228 formed continuously with the tip 225, and the arm 17 At the stop position where the arm 16 is stopped by the stopper 39, the cam surface 228 and the cam surface 227 of the arm 16 are in complete contact.

In this way, at the stop position where a large impact load including motor rotational inertia acts, the large cam surface 228 is brought into contact with the tip 225 to prevent wear and deformation of the tip 225.
It is possible to obtain stable performance over a long period of time.

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

During manual locking and unlocking, the arm 16 of the lever 17 runs idly between the tips 225 of the convex portions 45 mentioned above.

At the locked and unlocked positions, the stopper 39 is elastically deformed by further load in the direction of activation, the gap 230 is eliminated, and the motor is driven with the arm 16 within the rotation trajectory of the wheel gear tip 2250. When the switch is operated, the tip portion 225 and the arm 16 interfere with each other, and do not operate normally and may damage or damage their contact surfaces.

In the embodiment, since the arm 16 is provided with the extension part 229,
Even if an overload is applied, it will not fall within the operating trajectory of the wheel gear, and normal operation can be ensured by operating the switch.

Further, by setting the gap 230, the arm and the convex part do not interfere with each other during normal manual operation, so there is no sound of the resins hitting each other, and a good operation feeling can be obtained.

A switch that detects locking and unlocking by key operation will be described in detail. No. 22゜47.23.
48.49Refer to Figure 48.49. The detection switch 205 includes a main body 207 fixed to the housing 2' by a screw 206 or the like, and is rotatably supported by the main body 207, with one end 2
08 is inserted into the hole 209 of the key operation lever 13, and the movable part 21 operates in conjunction with the rotational operation of the key operation lever 13.
0, and has a contact part and a conductive part similar to those shown in FIG. 21 inside, and detects the locked and unlocked positions.

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

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

A substantially U-shaped groove 214 is formed by walls 215 and 216, serves as a passage for the wire harness 211, and is continuous with a passage 217 provided in the side wall. A clip 218 is locked to the wall 215, and its upper end piece 219 closes the opening of the groove 214 to prevent the wire harness 211 from jumping out of the groove 214. Note that FIG. 60 is a view seen from arrow N in FIG. 47.

The wire harness 211 is fixed to the housing with a clamp 186 as shown in FIG. 57, similar to the embodiment shown in FIG. 51.

In this way, the wire harness 211 is firmly held on the upper surface of the housing 2' by the clip 218 and the clamp 186, and sufficient space can be given to the glass lifting trajectory 114 in FIG. It is possible to obtain a compact door lock that requires less space and has a high degree of freedom in placement on a vehicle.

If there is sufficient space between the door glass lifting path 114 and the side surface of the housing for the wire harness 211 to pass through, the wire harness 211 can be attached to the hook 231 provided on the housing 2 as shown in FIGS.
By locking the harness, it is possible to prevent the harness from floating freely from the surface of the housing 2', and the number of parts and assembly work are cheaper compared to the one using the clamp 186 shown in Fig. 22.48. .

Please refer to FIGS. 47, 23, and 24. The rotation of the key operation lever 130 is transmitted to the protrusion 15 of the locking arm 9 through the protrusion 14 and step 14', thereby causing the locking arm 9 to rotate.

In order to ensure a sufficient gap with respect to the glass elevation locus 114 in FIG. 24, the switch 205 needs to be placed closer to the door lock.

As shown in FIG. 23, the protrusion 15 is bent toward the housing 2' in order to overlap the switch 205 near the rotation center of the key operating lever 13 and the locking arm 9. A recess 220 is provided between the operating range of the protrusion 15 in order to ensure a gap between the protrusion 15 and the protrusion 15.

By adopting this arrangement, the switch 205 can be moved closer to the door lock side.

In addition, a recess 221 is provided on the bottom surface of the movable part 210 of the switch 205.
By providing this and avoiding interference between the locking arm 9 of the output shaft 10 and the caulking portion 222, the switch 205 can be moved further toward the housing side.

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

The main body part 207 is provided with a boss part 223 extending toward the mounting surface of the housing 2', and is provided with a hole 224 into which the boss part 223 provided on the housing 2' is inserted to determine the position of the switch 205. ing.

In this manner, the boss portion 223 and the hole 224 allow the switch 205 to be installed in a correct relationship between the one end 208 of the movable portion 210 and the hole 209 of the key operation lever 13, thereby accurately detecting locking and unlocking.

Please refer to FIGS. 29 and 51. 184 is the motor 26
, is a wire harness wired to the conductive part of the board 122, and is fixed to the housing with a clamp 186 that passes through a clamp hole 185 formed in the housing 2.2'. Therefore, when assembling it to a vehicle, it is necessary to pull the connector (not shown) at the end of the wire harness and connect it to the mating connector, or to hold the connector.
Even if the door lock body is hung, this tensile load is borne by the aforementioned clamp 186 and does not extend to the part housed in the housing, so the tensile load is borne by the clamp 186 and does not extend to the part that is connected to the motor or the conductive part of the board. By not causing damage to the wire, it is possible to prevent immobility due to wire breakage.

FIG. 52 shows an O inserted along the groove 118 of FIG. 24.
a harness holding part 198 showing a ring 119, through which a wire harness disposed at the conductive part of the motor and the board passes;
Grip part 1 that improves workability when inserting into groove 118
99 are available.

FIG. 53 shows details of the grip part 199 with protrusions 20 on the outer periphery.
0 is provided, and the diameter 201 is set to be slightly larger than the width of the groove 118 described above. In order to reduce the outer diameter of the drive unit, the groove 118 has a meandering shape with few straight parts as shown in FIG. Due to the restoring force of trying to return, it jumped out of the groove, making it extremely difficult to work with.

In the embodiment, by providing several grips 199 with an outer diameter larger than the groove width, it is possible to prevent the above-mentioned phenomenon of protruding from the groove, and the insertion work is greatly improved, and the housings 2 and 2' It will not get caught outside the designated position, impairing the sealing performance, allowing water, debris, etc. to enter the housing, and reducing the function of the drive unit.

FIG. 54 shows the N homeland of FIG. 52, and is provided with a hole 202 through which the wire harness passes.

FIG. 55 is a cross section taken along line PP in FIG. 54, and a convex portion 203 having a diameter smaller than the outer diameter of the harness is provided inside the hole 202.

Figure 56 shows the harness holding part 19 in the housing 2.2'.
8 is attached, and the housings 2 and 2' are provided with protrusions 204 and 204', which press against the harness holding part 198.

Rainwater and dust cannot enter between the harness and the hole 202.
This is prevented by the protrusion 203 and also by the protrusion 204.204' between the harness holding part 198 and the housing 2.2'.

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

(Effect) When driving force is transmitted through contact between the wheel gear convex part and the arm part of the lever, the lever ratio can be improved by making contact between the convex part closer to the rotation center and the arm part farther from the rotation center. The required output of the motor is reduced, and the motor can be made smaller.

By forming the arm portion into a substantially V-shape toward the tip, the contact point can be set at a position further away from the rotation center of the arm portion.

By setting the trajectory of the tip of the arm so that it interferes with the convex part of the wheel gear, it is prevented from entering the rotation trajectory of the wheel gear mentioned above, so the motor can operate normally, and therefore the output shaft and Abnormal loads are not applied to levers, etc., and performance can be guaranteed over a long period of time.

During assembly work, by temporarily receiving the turnover spring force, the position of the lever during the work of fastening the housings together is restricted, which improves the ease of assembly.

Furthermore, since there is a gap between the arm and the convex part, the two do not come into contact during normal manual operation, resulting in quiet operation and an excellent feel of operation.

If you try to place the contact point of the wheel gear convex part as close to the center of rotation as possible, the shape will not have enough strength, like the tapered tip 225 shown in Fig. 46, which has a rounded tip. cannot sufficiently withstand the shock load, including the motor inertia load, that is applied when the motor's operation is stopped.

[In example 1i, the tip side from the contact point at approximately the middle position of the operating range of the lever of the arm is formed to be thinner toward the tip, so that the cam surface 22
8, and at the stop position where the impact load is applied, it comes into contact with the surface, which prevents the abrasion and breakage of the convex portion and provides stable performance over a long period of time.

[Brief explanation of the drawing]

Fig. 1 is a front view showing this example, Fig. 2 is a partial front view showing a state in which the open lever is operating the release lever, and Figs. 3 and 4 are partial front views showing the locking mechanism in a missed state. , Figures 5 and 6 are partial front views showing the keyless lock mechanism, Figures 7 and 8 are partial front views showing the self-cancelling mechanism, Figure 9 is an exploded view of the actuator section, and Figure 10 is a partial front view showing the self-cancelling mechanism. A plan view showing the return spring, Fig. 11 is a side view of the worm, Fig. 12 is an exploded perspective view of the attachment part of the output shaft, Fig. 13 is a side view showing the installation of the turnover spring, and Fig. 14 is the actuation lever. 15 is a graph showing the relationship between wheel rotation angle and motor reverse torque, FIG. 16 is a sectional view of the output shaft portion, and FIG. 17 is a plan view of the actuator portion. Figure 18 is a front view of the storage part of the door lock device.
Fig. 19 is a front view of the door lock device, Fig. 20 is a partial sectional view showing the O-ring between both housings, Fig. 21 is an enlarged partial plan view of the switch section, and Fig. 22 (a) is the door lock device. 22(5) is a partial perspective view of the switch section, FIG. 23 is a side sectional view of the actuator section, and FIG.
25 is a partial cross-sectional view showing the screw fastening portion, FIG. 26 is a cross-sectional view of another portion of the screw fastening portion, FIG. 27 is a cross-sectional view showing the stopper in the retracted state, and FIG. 28 is a view seen from arrow S-8 in FIG. 16, FIG. 29 is a plan view of the door lock device as seen from the vehicle mounting surface side, FIG. 30 is a plan view showing the support structure of the motor and worm gear shaft, and FIG. Fig. 31 is a cross-sectional view taken from arrow D-D in Fig. 30, Fig. 32 is a cross-sectional view taken from arrow E-E in Fig. 20, and Fig. 33 is a cross-sectional view taken from arrow F-F in Fig. 20. 34 is a cross-sectional view taken along the arrow GG in FIG. 20, FIG. 35 is a partial plan view showing the meshing of the worm gear and wheel gear, and FIG. FIG. 37 is a partial plan view showing the state in which the worm gear is transversely displaced, FIGS. 38 and 39 are plan views showing the reaction forces acting on each part, and FIG. 40 is a partial plan view of the state shown in FIG. Arrow view H
Figure 41 is a diagram showing the component force when viewed from the direction of arrow J in Figure 38. Figure 42 is a diagram showing the component force when viewed from the direction of the arrow in Figure 39. , Figure 43 is Figure 39
Figure 44 is a diagram showing the component force seen from the arrow direction in the figure, Figure 44 is a diagram when the tooth line is reversed, and Figure 45 is a diagram viewed from the direction of Figure 39.
The figure is a view from the opposite direction in Figure 39 when the tooth lines are reversed, Figure 46 is a plan view showing the relationship between the operating lever and the wheel, Figure 47 is a plan view of the housing part, and Figure 48 is the wire 49 is a sectional view showing the passage of the wire harness, FIG. 50 is a sectional view of the mounting part of the switch part, FIG. 51 is a sectional view of the clamp part of the wire harness, and FIG. 52 is a sectional view showing the wiring harness passage. 0-'J song overall map, 5th
Figure 3 is a cross-sectional view taken along the line Q-Q in Figure 52, Figure 54 is a view taken from arrow N in Figure 52, Figure 55 is a view seen from arrow P in Figure 54, and Figure 56 is a wire harness holder. Fig. 57 is a sectional view of the clamp part of the wire harness.
8 is a partial perspective view showing the hook of the housing, FIG. 59 is a side view showing the clamp portion, and FIG. 60 is a view seen from arrow N in FIG. 47. In the figure = door lock device, 2.2'...housing, 3
- Release lever 5 - Oven lever 8 Locking button, 9 - Locking arm, 10 Bin, 13 -
Key operation lever 15. Projection, 17 - Actuation lever, 2
4-Return spring, 26 Motor, 27-Worm gear, 34-Bearing section, 36 Turnover switch, 39-Stock collar, 159- Elastic material, 166...
・Backlash, 225-tip, 226.227.
228 Cam surface.

Claims (2)

[Claims] (1) A worm gear that has an actuator whose output shaft is connected to a link mechanism that operates the door lock mechanism, and the actuator is fixed to an electric motor, a wheel gear that meshes with the worm gear, and a convex portion formed on the wheel gear. In the door lock device, the convex portion is initially connected to the arm portion, and the door lock device includes an arm portion that can be freely engaged with the output shaft, and the output shaft has the rotation center at a position apart from the rotation center of the wheel gear. A door lock device comprising a contact point that contacts the arm portion and a contact surface that makes final contact with the arm portion. (2) The door lock device according to claim 1, wherein the tip of the convex portion contacts the base of the arm when the arm overstrokes.