JPH0291379A - Door lock device - Google Patents

Abstract

PURPOSE:To obtain a door lock device having an improved relationship with the fastener of a weather strip by adopting a means for forming a recess part on a part of housing above a motor storage part and faced to a door panel and using the recess part for supporting the head of a clip. CONSTITUTION:A groove 118 having an approximate L-shape is formed along the inner edge of a main housing 2 and a rubber O-ring 119 is inserted in the groove 118 and the O-ring 119 is flexed with the mating face 115 of a sub- housing 2', thereby ensuring sealing pressure. In addition, a recess part 191 as much recessed as possible is provided in a space formed above the motor storage part of the housing 2 and a clearance from the tip 190 of a clip is thereby maintained. Namely, it is possible to provide a recess part for the prevention of interference with the clip for fitting a weather strip by so positioning an operation lever as to be clear of the upper part of the motor storage part. According to the aforesaid construction, the degree of freedom is enhanced for arrangement in a vehicle as the substantial thickness of an actuator part is reduced. Also, the weather strip can be rigidly and stably retained and the high sealing performance thereof can be ensured.

Description

[Detailed description of the invention] (Industrial application field) The present invention relates to a door lock device with a reduced thickness.

(Prior Art) A door lock device, which has a housing that houses a door lock engagement part and an actuator part that makes the door lock lockable and unlockable, is installed in a limited space between the vertical path of the door window and the center pillar. It can be fixed to the door panel by positioning it. Therefore, it is desired that the door lock device be small and thin.

On the other hand, the space between the door panel and the body panel is sealed with a weather strip, and when fishing by boat, the weather strip is fixed to the door panel with double-sided tape or clips.

(Problem to be solved by the present invention) Car body designs have become three-dimensionally complex (
As vehicles become more popular, clips are used instead of double-sided tape to support weatherstrips on body panels, since double-sided tape, which tends to attract dust, cannot be used to attach weatherstrips along the correct path. but,
Since the head of this clip protrudes toward the door lock device, it is necessary to shift the door rotor device toward the door window elevation trajectory, which makes the door lock device thinner. As the number of functions and number of parts increases, there is a limit to how thin a device can be made.

SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a door locking device that has an improved weatherstrip connection.

(Means for Solving the Problems) In order to solve the above-mentioned problems, the present invention employs means for forming a recessed portion in a part of the housing that is above the motor storage portion and faces the door panel. This recess receives the head of the clip.

(Function) Since the position of the housing can be determined by fitting the head of the clip into the recess of the housing, assembly work is easy.

(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 roughly shaped 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 ball of a door lock actuating unit including a ratchet and a ball (not shown), and the release lever 3 is interlocked with the ball via a pin 27. When the door is closed, the aforementioned ball 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 FIG. 1 is such that the latch of the door lock and the ball are engaged, and by rotating this lever 3 counterclockwise, the ball rotates the ratchet, causing the latch and the ball to engage. 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 30 pushes down the open lever 5 pivotally attached to one end of the lever 30. This downward movement of the open lever 5 is achieved by the protruding 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 26. The door lock is placed in the latch release state and the door can be opened (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 open lever 5 via an elongated hole. Locking arm 9 is the first
When in the position shown, the lowering of the open 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 around the pin 10 together with the pin, the open 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, even if the handle is operated to lower the open lever 5, the protruding piece 6 and the end 7 do not come into contact with each other and the door lock remains engaged. (See Figure 4).

The keyless rotor 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.
The protruding piece 12 is activated, and the release lever 3 freely rotates counterclockwise, thereby maintaining the lock of the door. (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. While the door is open, press the locking button 8, rotate the locking arm 9 clockwise, and rotate the oven 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 rotor actuating section (not shown). This movement causes the protrusion 12 of the release lever 3 to come into contact with the step 11 of the open lever 5, causing the oven 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 oven lever 5 pushes down the end 7 of the release lever 3, and the lever that enables the opening of the door is pressed down. Set to locked state.

Key operations will be described with reference to FIG.

The key operation lever 13 is rotatably supported in the housing 2', and its protrusion a1314 is connected to the protrusion 1 of the locking arm 9.
5 in parallel. 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 moves clockwise from A to B.
position, the locking arm 9 is rotated clockwise by the contact between the protrusion 14 and the protrusion I5, and the locking state of the door lock is ensured. The key operating lever 13 returns from position B to position A by the action of a spring attached to. That is, the locking button 8 is pressed down, in other words, the protrusion 6 of the open lever 5 and the end 7 of the release lever 3 are not opposed, even if the outside or inside handle is operated. , the door remains closed. 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. Note that even if the key operation lever 13 is rotated to the position B' using the key in the state shown in FIG.
' is only brought close to the protrusion 15, but the locking arm 9 does not rotate.

In addition to the above-mentioned manual operation, the locking and unlocking states can be achieved by electrically rotating the pin 10 and rotating the locking arm 9 clockwise (or vice versa) in response to an instruction signal from the driver. What you get is done. 91st! See l. Actuation lever 1 with arm B16 on pin 10
Fix 7. Wheel gear 18I rotatably supported by the housing - both ends 19.20 of the pair of raised protrusions
is opposed to the downward arm portion 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. 1O, 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 rotation of the operating lever 17 and pin 1o, allowing the locking arm 9 to move from position A to position B. Make it. When the wheel gear 18 rotates 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 2o causes the actuating 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 γ0 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. The lead angle of the worm gear 27 (γ0
) 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 actuation lever 17 and the wheel gear 18 are completely separated during manual operation, the arm portion 16 only runs idle between the ends 19 and 200 of the 450 pairs of convex portions, and does not pull the motor portion. , easy to operate 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. When the pin 10 is inserted into the bearing part 34, the rectangular part of the pin 10 that protrudes from the bearing part 34 is inserted into the hole 35 of the same shape in 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. 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 opposite to this recess 37. In this example, since the pin IO 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 rotation center of the release lever 3, also serves as the rotation center of the ball of the door lock operating section (not shown), and the pin 27, which can freely come into contact with the ball, rotates the ball. 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.
Stoppers 39 for stopping the operating lever 17 are arranged at these positions (B, B'). The function of this stopper 39 is
This will be explained with reference to FIG. 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 actuation lever 17 to be rotated together with the pin 10 by the end 19 of the convex portion 45. 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 regular stop position 40, the actuating lever 17 and the stopper 39 come into contact and try to prevent the movement of the actuating lever 17, but due to the rotational inertia of the motor, the stopper 39 The actuating lever 17 moves to the overtravel position 41 while elastically deforming the actuating lever 39 .

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 nozzle ring 2' consists of a large opening 42 for receiving the large shaft diameter portion 40 and a small opening 43 for receiving the small shaft diameter portion 41. A locking arm 9 is fixed to a small shaft diameter portion 41 protruding from the housing 2', and a key operating lever 13 is rotatably supported by a bearing portion 34 of the housing 2'.

When installing the pin IO 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 lO into the hole 32. The output shaft 10 is inserted into the hole 32 using 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, the movement of the pin IO 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
6.1? As shown in the figure, 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 renocou 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 operating lever 17 is in the locked or unlocked position and the power to the motor 26 is turned off, the releasing force of the compressed return spring 24 is applied to the wheel 18, the worm 27, and the motor 2.
6 and return the wheel 18 to the neutral 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, the convex portion 45 is connected to the operating lever 17.
When it comes into contact with the arm 16 of the motor, the rotational inertia energy of the motor can be transmitted to the arm 16, thereby making it possible to downsize the motor.

Although the door lock device 1 has been described, FIG.
The mounting portion of the door lock device 1 will be explained with reference to . 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 9. The striker 51 can be freely engaged with and disengaged from a ratchet (not shown) of the door lock device 10 when the front door 47 is opened or closed. On the other hand, the windshield 52 of the front door 47 moves along a locus 53 along the center pillar 49 when it goes up and down. Therefore, the door lock device 1 fixed to the front door 47 side needs to avoid the trajectory 53 of the windshield 52 to prevent interference between the windshield 52 and the door lock device 1. 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. The lock device 1 is stored. That is, the door lock device 1 needs to have an external shape that fits within the limited space of the projecting portion 55. 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 together, improving sealing performance, and also improves sealing performance between the output shaft and the bottle 10. To prevent misalignment with the pin receiving hole of the housing 2.

Referring again to FIG. A substantially U-shaped groove 11g is arranged along the inner edge of the main housing 2, a rubber O-'J song 19 is inserted into this groove 118, and the O-ring is inserted into the mating surface 115 of the sub-housing 2'. 119 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 rainwater or dust from entering the housing 2. . This wall 120 is also effective in improving 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 the entire surface of the arm portion and the housing being illuminated.

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 two-position detection accuracy is improved. Since the arm portion 124 of the operating lever 17 is arranged to avoid overlapping with the protrusion 129 that fixes the contact 123, the board and the arm portion can be brought as close as possible, and the height of the drive portion can be reduced. .

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 storage 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 192.

As shown in FIGS. 17, 24, and 25, the housing 2' has a screen L192 penetrated therethrough.
The hole ring 2 is provided with a hole 193 that is larger than the outside diameter of the screw L192, and a fastening hole 194 that is slightly smaller than the outside diameter of the screw L192.

Refer to FIG. 26. By fastening housings 2 and 2'
In order to prevent this relationship from shifting, the diagonally arranged holes in the housing 2' are made into holes 195 that are slightly smaller than the outer diameter of the screw 192, so that when the screw L192 is tightened, the slurry is automatically removed. The structure is such that the shaft center and hole center coincide.

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 bearing part 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 of 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 lock mounting surface 116 of the door panel houses a well-known engagement mechanism for keeping the door closed.

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

At the bottom of the groove 180, there is a water channel 182 with the bearing part 181 of the pin 10 as close to the door panel 113 as possible.
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, it is possible to reduce the stiffness of the door lock actuator part in the longitudinal direction of the vehicle, and it is possible to secure a gap between the door glass and the ascending/descending path 114. It can be placed higher up to improve the strength of the upper part of the door against collisions, etc., or it can be placed to the rear of the door from the vertical path, increasing the door glass area and increasing the degree of freedom in design. Can be done.

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 and to receive the tip of the shaft 100 and the washer lot when caulking, the other end 105 protrudes outward from the surface of the housing 2', allowing rainwater etc. to enter from the gap. 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.

Furthermore, in order to prevent interference between the winding 144 and the case 137, the collar 146 is placed between the core 145 and the winding 144. It is arranged. The Mazda net 14 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 fixed to the knurling 151 and prevents the resin case 138 from cracking, and it also absorbs the thrust load generated during locking and unlocking operations and improves durability. It is effective for

Support part 13 that supports bearing part 137' of case 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 of 1530 minutes 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.
A gap 153 between the collar 146 and the end face of the bearing 141 is provided between the collar 146 and the support part 134 to absorb manufacturing errors between the motor shaft length 154 and the length 155 to the thrust load receiving surface of the support part 134. Gap between smaller gaps 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 way that there is a clearance between the motor case and the motor case to account for the amount that cannot be absorbed by zero elastic deformation, and when the motor is assembled, the case 138 and the support section 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 64 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 will be 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 engine is struck. An impact load containing the rotational inertia energy of the motor 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 actuating 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.

An arrow 168 indicates a reaction force from the stopper 39 to the actuating lever 17, and an 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.

Figure 43 is the L homeland in Figure 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 1750 described above, the engagement is prevented from becoming shallow.

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. 40.42, the actuating lever 17
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. The taper of the convex portion 45 of the wheel gear 18 that runs idly between the gap 46 makes contact with the rounded tip 225 and the substantially V-shaped cam surface 226 that widens toward the tip of the arm 16. come into contact with The approximately 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 as possible from the center of rotation of the lever 170.

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 side of the lever 17 and the tip portion 225, and also, on the rotation trajectory of the lever 170, It is arranged so as to interfere with the extension part 229 and the tip part 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 rotational trajectory of the wheel gear tip 225. When the switch is operated, the tip 225 and the arm 16 interfere,
It may not operate normally and may damage or damage the respective 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 part 207 fixed to the housing 2' by a screw thread 206 or the like, and is rotatably supported by the main body part 207.
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 13 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 lifting 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 winter switch 205 near the rotation center of the key operation lever 13 and the locking arm 9. In order to ensure a clearance between the projection 15 and the housing 2', a recess 220 is provided within the operating range of 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 IO 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 provided 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 the 0
- Harness holding part 198 showing the ring 119, through which the wire harness disposed at the conductive part of the motor and the board passes through.
and a grip portion 199 that improves workability during insertion into the groove 118.

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 to its original shape, it would pop out of the groove, resulting in very poor workability.

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.

(Effects) In the present application, by arranging the operating lever so as to avoid the upper part of the motor housing, it is possible to provide a concave portion that prevents interference with the weatherstrip mounting clip, and the substantial thickness of the actuator portion can be reduced. Since it is thin, there is a high degree of freedom in its placement on the vehicle, and the weather strip can also be firmly and stably held, ensuring high sealing performance to prevent rain leakage and intrusion of debris.

[Brief explanation of drawings]

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 the wheel rotation angle and the motor reverse torque, FIG. 16 is a sectional view of the output shaft portion, and FIG. 17 is a plan view of the actiniator 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) is a partial perspective view of the switch section, FIG. 23 is a side sectional view of the actiniator section, FIG. 24 is a plan view of the actiniator section, and FIG. 25i! i0 is Sufu I
J, - A partial sectional view showing the fastening part, Fig. 26 is a sectional view of another part of the screeny fastening part, Fig. 27 is a sectional view showing the stored state of the stopper, and Fig. 28 is a view taken in the direction of arrow S in Fig. 16. -3
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. 31 is the arrow D- in FIG. 30.
32 is a sectional view taken from arrow direction D in FIG. 20, FIG. 33 is a sectional view taken from arrow direction FF in FIG. FIG. 35 is a partial plan view showing the meshing of the worm gear and wheel gear, FIG. 36 is a partial plan view showing the pitch between both gears is increased, and FIG. 37 is a cross-sectional view taken from arrow GG. 38 and 39 are plan views showing the reaction forces acting on each part, and FIG. 40 is the component force when viewed from the direction of arrow H in FIG. 38. FIG. 41 is a diagram showing the component force seen from the direction of arrow J in FIG. 38, FIG. 42 is a diagram showing the component force seen from the direction of arrow J in FIG. Diagram showing the component force seen from the direction of the arrow in the figure, No. 44
The figure is a view from the direction of Figure 39 when the tooth line is reversed, Figure 45 is a view from the L direction of Figure 39 when the tooth line is reversed, and Figure 46 is the operating lever and wheel. 47 is a plan view of the housing section, FIG. 48 is a sectional view showing the wire harness clip, FIG. 49 is a sectional view showing the passage of the wire harness, and FIG. 50 is the installation of the switch section. Figure 51 is a cross-sectional view of the clamp part of the wire harness, Figure 52 is an overall view of the O-9 ring, Figure 531! l is a sectional view taken along the line Q-Q in FIG. 52, FIG. 54 is a view taken from arrow N in FIG. 52IIQ, FIG. 55 is a view taken from arrow P in FIG. 57 is a sectional view of the clamp portion of the wire harness, FIG. 58 is a partial perspective view showing the hook of the housing, FIG. 59 is a side view showing the clamp portion, and FIG. It is a figure seen from view N. In the diagram: 1. Door lock device, 2.2'...Housing, 3. Release lever, 5-Open lever 8.
...locking button, 9...-locking arm,
10...Bin, 13...Key operation lever 15.
・Protrusion, 17... Operating lever, 24... Return spring, 26... Motor, 27... Worm gear, 34-... Bearing part, 36 Turnover switch, 39... Stroke 7/( , 159... elastic material, 166-...
・Backlash, 225・-1, tip, 226.2
27.228 Cam surface. Agent Patent Attorney Hideaki Kuwahara Figure 11 Figure 18 Figure 31 Figure 34 Figure 42 Figure 39 Figure 48

Claims (2)

[Claims] (1) It has one housing that pivotally supports the output shaft of the actuator part that makes the door lock lockable and the other housing that houses the drive part of the actuator part, and the fixed housing is supported by the door panel. In this door lock device, a recess is provided in the upper outer surface of the electric motor receiving portion of the housing on the door panel side. (2) The door lock device according to claim 1, wherein the recess receives a clip for attaching the door weather strip to the door panel.