JPH0291376A - Door lock device - Google Patents

Abstract

PURPOSE:To prevent the jumping of an O-ring out of a groove by adopting a means for providing a grip part at a part of the O-ring and more preferably the retaining part of a wire harness in the O-ring. 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 aforesaid groove 118. In addition, the O-ring 119 is flexed with the mat- ing face 115 of a sub-housing 2', thereby ensuring sealing pressure. In this case, a grip part having a diameter slightly larger than groove width is provided in a part of the O-ring 119 and this O-ring 119 is retained against the stability thereof via the insertion of the grip part in the predetermined position of the groove 118. According to the aforesaid construction, workability can be substantially improved and sealing performance can be ensured.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a door lock device with an improved housing.

(Prior Art) A door lock device has an electric actuator section that creates a lockable/unlockable state, and at least this actuator section is configured to be housed in a half-split housing.

Since the electric actuator uses a lubricant in addition to each electrical component, it is necessary to prevent rainwater and the like from entering from the mating surfaces of the pair of housings. For this reason, an O-ring is interposed on this mating surface.

(Problems to be Solved by the Present Invention) Since the door lock device is fixed to the door panel and is located in a limited space between the windshield elevation track and the center pillar, it is necessary to make its external shape as small as possible. Therefore, each part has a complicated shape, and the planar shape of the mating surface of the housing also draws a complicated curve. Even if an 0-ring is inserted into a groove formed on a mating surface formed with such a curve, the restoring force of the 0-ring to return to its straight line causes it to pop out of the groove, resulting in extremely poor workability. .

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

(Means for Solving the Problems) In order to solve the above-mentioned problems, the present invention basically employs means for providing a grip portion in a part of the O-ring. Preferably, this O-ring 12 wire ≠ gear harness holding portion is provided.

(Function) Since the grip part is slightly larger than the groove width, when this grip part is inserted into the groove, it can be firmly held against the groove.

(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 open lever 5 pivotally attached to one end of the lever 30. The downward movement of this open lever 5 is 1. The protruding piece 6 at the center of the open lever 5 is 11 m7 from the release lever 3.
is pressed, and the release lever 3 is rotated counterclockwise about the fulcrum 26 to bring the door lock into the latch release state and allow the door to 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 a long length. 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 together with the bottle around the bottle 10, 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 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 stepped part 11 of the open lever 5 and the protrusion 12 of the release lever 3 (7) are hit dry, and the release lever 3 is free to move. It will rotate counterclockwise to keep the door 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 rod. 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 i operation lever 13 returns from B to A position 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 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.
The locking arm 9 only approaches the protrusion 15, and the locking arm 9 does not rotate.

In addition to the above-mentioned manual operation, the pin 1o is electrically rotated in response to an instruction signal from the driver to rotate the locking arm 9 clockwise (or vice versa) to enable locking and unlocking. What is gained is achieved. See FIG. 9. An operating lever 17 having an arm portion 16 is fixed to the pin 1o. Both ends 19.2o of a pair of protrusions erected on 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 partly narrowed by opposing wall surfaces 22 and 23.

The coil spring 24 is placed in the groove 21 and its end rests against the shoulder of the wall 22.23. Furthermore, wheel gear 1
A projecting piece 25 protruding from the lower surface of the wall 8 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 allows the spring 24
It has a long overall length to ensure sufficient flexibility.

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 T0 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 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 section 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 opposite to this recess 37. 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.
Stoppers 39 for stopping the operating lever 17 are arranged at these positions (B, B'').The function of these stoppers 39 will be explained with reference to FIG. 14.In addition, in FIG. 14, only one stopper 39 is shown. However, since the function of the other stopper is the same, 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 normal stop position 40, the actuating lever 17 and the stopper 39 come into contact and attempt to prevent the actuating lever 17 from moving, but the rotational inertia of the motor causes the stopper 39 to 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 IO, which is an output shaft fixed to the actuation lever 17, has a stepped configuration 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 IO, 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, 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 IO 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 1'8 returns to the neutral position, as shown in FIG.
A gap 46 is left between the end of the convex portion 45 and the arm 16. 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 l fixed to the front door 47 side avoids the trajectory 53 of the windshield 52, and
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 l is connected to this projecting portion 5.
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 disposed 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, and 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 placed on the operating lever 17 that is directly connected to the locking lever 9 that switches between locking and unlocking, it is possible to improve the accuracy of detecting one position. 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 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 192.

As shown in FIGS. 17, 24, and 25, the housing 2' has a screw 192 that passes through the housing 2'.
The hole 193, which is larger than the outer diameter of the ring 2, has a hole 193 larger than the outside diameter of the hole 193. Fastening hole 194 slightly smaller than the outer diameter of J5192
It has.

Refer to FIG. 26. By fastening housings 2 and 2'
In order to prevent the relationship from shifting, the hole in the housing 2' arranged diagonally is made into a hole 195 that is slightly smaller than the outer diameter of the screw 192, so that when the screw L192 is tightened, it will automatically align with the center of the screw shaft. It has a structure in which the hole center coincides with the hole center.

In this way, by using the centering structure that is inexpensive and does not take up much space, the bottle 10 that is caused by 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 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 in the closed state of the door lock.

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, the bearing of the pin lO is placed in the water channel 182 with the portion 181 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, the thickness of the door lock acticoator part in the longitudinal direction of the vehicle can be reduced, and a gap between the door glass and the vertical path 114 can be secured, and the door lock device can be It can be placed higher up on the door 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 freedom of design. It can be increased.

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 101 when caulking, the other end 105 protrudes outward from the surface of the housing 2', so that rainwater etc. A flange portion 106 is provided to lengthen the path for insertion and prevent rainwater from entering.

FIG. 17 is a view from inside the housing 2',
Pin 10. The positional relationship between the operating lever 17, the wheel gear 18, the motor 26, and the worm gear 27 is shown, and as is clear from FIG. The worm gear 27 and the motor 26 are mounted on 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, since the positional relationship of the drive transmission system and especially the meshing relationship between the single wheel gear 18 and the worm gear 27 are determined only by the sub-housing 2', manufacturing errors such as the pitch distance between the gears can be minimized. This enables smooth power transmission, which in turn allows for a public service type system with less motor exit loss.

The motor support structure will be explained in detail in the 30th ffl.

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 1370 by press fitting or the like, and a bearing part 1 of the case 13B.
It is rotatably supported by a bearing 14.2 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.

Magnet 14# is fixed to 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 15t of the motor shaft.
It resists the load when the worm gear 27 is firmly fixed to the knurl 151 provided in the l, and prevents cracking of the resin case 138, and also receives the thrust load generated during locking and unlocking operations, improving durability. 1 is valid.

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, the thrust direction position of the motor and the positional relationship with the shaft 1"00 that pivotally supports the wheel gear 18 are determined.

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 collars 14 and 6 and the bearing 141, which would cause various output losses, there are Motor shaft length 154
The thrust load receiver of the support part 134 has a length of 155 to the surface.
In addition to absorbing manufacturing errors between the collar 146 and the bearing 1,
A gap 156 is set, which is smaller than the gap 153 between the end faces of 41.

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 14
Contact between the end faces of the bearing 6 and the bearing 141 is avoided, thereby preventing an increase in rotational resistance, preventing loss of motor output, and reducing the size of the motor.

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.

Also, in the radial direction of the shaft portion 152 of the worm gear 27,
A small gap is set between the support part 134 and, for example,
The operating lever is stopped at the locked and unlocked positions,
They come into contact when the pitch distance is about to increase due to the reaction force of meshing with the wheel gear 18.

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 B15
2, since the contact is released, there is no loss of return spring force in this part, and therefore the return spring force is small, and the motor can be made smaller. Also, what determines the normal motor axis is
Because of the support parts 132 and 133, 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, a support portion 157 is provided that comes into contact with the tip 152 of the worm gear when it 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 bent and arranged on the housing 2 side of the motor case 137 supported by the housing 2'.
If the dimension between the support parts 132 and the housing 2 is increased, or if the dimension 160 between the support parts 132 and 133 is increased and a gap is created between the motor case and the motor case, the door opening 1 This prevents the motor case from moving due to vibrations during driving, worm engagement reaction force when the motor is driven, etc., and causing abnormal noise.

Bearing 1138 of motor case 138 as shown in FIG.
A support portion 161 that supports ' is provided.

Next, the meshing between the worm gear 27 fixed to the motor shaft 140 and the wheel gear I8 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 complex 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 a reduction gear using small gears, for example, a module 0.6 (tooth depth 1.35 m + n) 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 tooth tips,
In particular, in the case of levers that drive levers that are restricted in operation by contacting a fixed object after a specified operation, when the motor is stopped, the motor rotation is abruptly stopped, so an impact load containing the rotational inertia energy of the motor is applied. However, the tooth itself may be damaged.

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.

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.

FIG. 43 is a view from H in FIG. 39, and shows 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 actuator section for the door rotor 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 lO.

The working relationship between the protrusion 45 and the arm 16 has been described in FIG. The contact point of the arm 16 with the convex portion 45 is preferably located as far from the rotation center of the lever 170 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 aforementioned 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.
48.49 Refer to Figure. The detection switch 205 has a main body 207 fixed to the housing 2' by a screw, E206, etc., and is rotatably supported by the main body 207. One end 208 is inserted into the hole 209 of the key operating lever 13, and the key is operated. It consists of a movable part 210 that operates in conjunction with the rotation of the lever 13, and has internal contact parts and conductive parts similar to those shown in FIG. 21 to detect 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 formed 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. Incidentally, FIG. 60 is viewed from the 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 rotor 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 clamp 186, it is possible to prevent the No. 1-nes from floating freely from the surface of the housing 2', and the number of parts is reduced compared to the clamp 186 shown in Fig. 22.48.
Easy to assemble and inexpensive.

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 elevation locus 114 in FIG. 24, the switch 205 needs to be placed closer to the door stopper.

As shown in FIG. 23, in order to overlap the switch 205 near the rotation center of the key operation lever 13 and the locking arm 9, the protrusion 15 is bent toward the /% Ujirin 2' side. In order to ensure a clearance between the protrusion 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 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 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
- A ring 119 is shown, and is provided with a harness holding part 198 through which a wire harness disposed on the conductive part of the motor and the board passes, and a grip part 199 that improves workability when inserting 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 1180 described above. The groove 118 has a meandering shape with few straight parts, as shown in FIG. 24, in order to reduce the outer diameter of the drive part.
When the O-ring was inserted and routed, the restoring force of the O-ring itself trying to return to its straight line caused it to protrude from 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 shown installed, and the no. 1 ring 2 and 2'
Convex portions 204 and 204' are provided on the harness holding portion 198 and press the harness holding portion 198.

Rainwater and dust cannot enter between the harness and the hole 202.
This is prevented by the protrusion 203 and by the protrusion 204, 204' between the nose retaining 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) In this application, a part of the 0-IJ song is provided with a grip portion with a diameter slightly larger than the groove width, so by inserting the grip portion into a predetermined position in the groove, the 0-IJ song can resist the restoring force. , the O-ring can be held in the groove, eliminating the possibility of the O-ring protruding, greatly improving work efficiency, preventing it from being caught in places other than the specified position, and furthermore, the grip part and the groove Since the position is connected to the position 7', there is no excessive tension, and the sealing performance is ensured.

[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 1O 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(b) is a partial perspective view of the switch section, FIG. 23 is a side sectional view of the actuator section, and FIG. 24(b) is a front view of the switch section.
The figure is a plan view of the actiniator section, FIG. 25 is a partial sectional view showing the screw fastening section, FIG. 26 is a sectional view of another part of the screw fastening section, and FIG. 27 is a sectional view showing the stored state of the stopper. , FIG. 28 is a view seen from arrow S-8 in FIG. 16, FIG. 29 is a plan view of the door lock device seen from the vehicle mounting surface side, and FIG. 30 is a plan view showing the support structure of the motor and worm gear shaft. , 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. 34 is a 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; FIG. Arrow view H in the diagram
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-Overview of the ring, No. 53
The figure is a cross-sectional view taken along the line Q-Q in Fig. 52, Fig. 54 is a view seen from arrow N in Fig. 52, Fig. 55 is a view seen from arrow P in Fig. 54, and Fig. 56 is a wire harness holding section. 5th cross-sectional view of
Figure 7 is a sectional view of the clamp part of the wire harness, No. 58
The figure is a partial perspective view showing the hook of the housing, FIG. 59 is a side view showing the clamp part, and FIG. 60 is a view shown by arrow N in FIG. 47.
This is a closer view. In the diagram: l... Door lock device, 2.2' - Housing, 3 - Release lever 5... Open lever 8
- Locking button, 9.・Rocking arm, 10
Bottle, 13--key operation lever 15 protrusion, 17-
Operating lever 24 return spring, 26-motor, 27-worm gear, 34-bearing section, 36-turnover switch, 39-stopper, 159...1 elastic material, 166-backlash, 225 tip, 226.
227.228 Cam surface.

Claims (1)

[Claims] (1) It has an actuator part that creates a locking/unlocking state with the engaging part of the door lock, and a pair of split housings that accommodate the respective parts, and a groove provided in one of the mating surfaces of both housings. A door lock device characterized in that an O-ring to be inserted has a grip portion that is slightly larger than the width of the groove.