JPH07122368B2 - Door lock device - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a door lock device having an improved actuator section.

(Prior Art and Problems to be Solved by the Present Invention) An actuator arranged at a lower portion of a door lock includes a housing through which an output shaft penetrates and a housing which cooperates with the housing and encloses an actuator mechanism. The dimensional accuracy of the pitch distance between the worm gear fixed to the and the wheel gear that meshes with this worm gear is
It is important to ensure the performance of the actuator, and it is important to ensure the output performance that the abutting relationship between the convex part of the wheel gear and the arm part of the operating lever is set at the set lever ratio. .

For example, in the case where the wheel gear is rotatably supported in the sub-housing and the motor is positioned in the main housing, the pitch distance between the wheel gear and the worm may vary due to the positional deviation during assembly of both housings. The small teeth used in the small speed reducer as shown in the example cause a malfunction such as immobility due to interference between the tooth bottom and the tooth top, or a decrease in tooth strength due to meshing between the tooth tops.

Conventionally, when bearing the tip of a motor shaft, high manufacturing precision is required to prevent center misalignment between the motor body support and bearing, and to prevent twisting of the shaft tip during rotation. When using it, preventing output loss at this bearing is an important issue for ensuring performance.In the radial direction, insert the bearing, or in the longitudinal direction, adjust the clearance finely with screws etc. The work was poor and the work was expensive.

Therefore, the present invention has an object to solve the above-mentioned problems.

(Means for Solving the Problem) In order to solve the above-described problems, the present invention provides a door lock device in which an actuator portion is housed in a lower portion of a main housing that houses a meshing portion for a door lock. An electric motor constituting the actuator portion in a sub-housing fixed to the lower part of the motor, a worm gear fixed to the motor shaft of the electric motor, a wheel gear meshing with the worm gear, and a protrusion of the wheel gear. A bearing that supports an operating lever, supports the end portion of the motor shaft in a radial direction and an axial direction with a gap, and supports a core that holds the winding of the electric motor and the motor shaft that is adjacent to the core. Provided is a door lock device in which a gap is provided between the gap and the gap between the former and the gap between the former and the latter.

(Operation) In the present application, since the sub housing is provided with the output shaft, the wheel gear support shaft, and the motor support portion, the dimensional accuracy between each element is determined by the molding die of the sub housing. It is not affected by misalignment, and visual work is possible even when engaging the teeth of the wheel gear and the worm when installing the motor. Damage the parts,
Without causing functional disorders or the generation of abnormal noise,
Stable performance can be obtained over a long period of time. Furthermore, by supporting each element of the drive transmission of the actuator in the housing, it is possible to easily obtain a substantially V-shaped arrangement in which the lower the vehicle goes, the more it comes out toward the front of the vehicle. This greatly increases the degree of freedom in vehicle design.

In addition, the bearing structure for the motor shaft has a small gap in the shaft radial direction, and normally the motor shaft is not supported and the motor shaft rotates and the operation of the actuator lever is stopped. , When the rotation resistance of the wheel gear increases and the motor shaft elastically deforms in the direction in which the wheel gear and the worm gear move away from each other, the motor gear is supported and maintains a meshed state. The gap is set to be smaller than the amount, and is supported when the motor shaft is moved in the longitudinal direction of the motor shaft due to the meshing reaction force between the worm and the wheel.

(Example) An example in which the concept of this example is applied to a door lock device will be described below. The door lock device 1 has a substantially L-shaped release lever 3 pivotally supported by a main housing 2 made of synthetic resin. The release lever 3 is rotatable about a fulcrum 26 at the center thereof. The fulcrum 26 is also the center of rotation of the pole of the door lock operating portion including a ratchet and a pole (not shown), and the release lever 3 is interlocked with the pole via the pin 27. In the door-closed state, the above-mentioned pole engages with the latch provided in the door lock operating portion that engages with the strike force attached to the vehicle (not shown). The position of the release lever 3 shown in FIG. 1 is in a meshed state in which the above-mentioned latch of the door lock and the pawl are in mesh with each other, and when the lever 3 is rotated counterclockwise, the pawl rotates the ratchet so that the latch and the pawl are connected. The latch release state in which the engagement of is released is obtained, and the door can be opened. When the outside handle is operated, a force acts in the direction indicated by 29, and the rod 4 pivots the lever 30 pivotally supported by the main housing 2 to the fulcrum 31.
Rotate counterclockwise around. When the inside handle is operated, a force acts in the direction indicated by 28 to rotate the lever 30 counterclockwise about the fulcrum 31. lever
The counterclockwise rotation of 30 pushes down the open lever 5 pivotally attached to one end of the lever 30. In the downward movement of the open lever 5, the protrusion 6 at the center of the open lever 5 pushes the end portion 7 of the release lever 3 to rotate the release lever 3 counterclockwise about the fulcrum 31.
The door lock is in the latch release state and the door can be opened (see Fig. 2).

To prevent the door from being opened accidentally while the vehicle is running,
Lock the door, but generally lock button 8
This door lock is formed by pressing and rotating the locking arm 9 interlocked with this in the clockwise direction. A part of the locking arm 9 is connected to the lower part of the open lever 5 through an elongated hole. Locking arm 9 is first
When in the position shown, the lowering of the open lever 5 allows the projection 6 thereof to abut on the end 7 of the release lever 3.
However, when the locking button 8 is pushed and the locking arm 9 is rotated clockwise around the pin 10 together with the pin 10, the open lever 5 moves in the direction of the arrow C, and the projecting piece 6 of the open lever 5 is moved to the end 7 of the release lever 3. Away from (see Figure 3). As a result, even if the handle is operated and the open lever 5 is lowered, the projecting piece 6 and the end portion 7 do not come into contact with each other, resulting in idle driving, and the door lock remains engaged. (See FIG. 4).

The keyless lock mechanism will be described. With the door open, push the locking button 8 and rotate the locking arm 9 clockwise to move the projection 6 to the release lever 3
The end portion 7 is not opposed. When the outside or inside handle is operated, the open lever 5 is pushed down and the state shown in FIG. 5 is obtained. When the door is closed in this state, the release lever 3 is rotated counterclockwise, but the step portion 11 of the open lever 5 and the projecting piece 12 of the release lever 3 become idle and the release lever 3 is freely rotated counterclockwise. Will rotate in the direction and keep the door locked. (See FIG. 6). After the door is closed, the release lever 3 will be in the state shown in FIG. 5 due to the spring in the door lock operating portion, and will return to the state shown in FIG. 3 when the operation from the handle side is stopped.

Next, the self-cancelling mechanism will be described. While the door is open, the locking button 8 is pushed to rotate the locking arm 9 clockwise, and the open lever 5 is rotated in the direction C shown in FIG. To do. When the door is closed without operating the outside or inside handle, the release lever 3 is rotated counterclockwise by the pole of the door lock operating portion (not shown). This movement causes the protruding piece 12 of the release lever 3 to come into contact with the step portion 11 of the open lever 5 to move the open lever 5 to the 8th position.
Rotate clockwise as shown. As a result, the locking button 8 is returned to its original position and the locking arm 9
Rotates counterclockwise about the pin 10 through the elongated hole of the open lever 5. That is, since the state shown in FIG. 1 is restored, 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 to enable the door to open. Locked.

The key operation will be described with reference to FIG. A key operation lever 13 is rotatably supported by the housing 2 ', and a protrusion 14 thereof is provided in parallel with a protrusion 15 of the locking arm 9. This lever 13 is connected at one end to the key cylinder via a rod. When the key is operated in the locking direction, the key operation lever 13 rotates clockwise from the A position to the B position, and the protrusion 14
When the locking arm 9 is rotated clockwise by the abutment of the protrusion 15 with the protrusion 15 and the locked state of the door lock is secured and the operation of the key is stopped, the key mounted by the spring mounted on the key cylinder side The operation lever 13 returns from the position B to the position A. That is, in a state where the locking button 8 is pushed down, in other words, the projecting piece 6 of the open lever 5 and the end portion 7 of the release lever 3 are not opposed to each other, and 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 the protrusion 15 and the locking arm 9 is rotated counterclockwise to the unlocked state shown in FIG. In the state shown in FIG. 1, even if the key operation lever 13 is rotated to the position B'by the key, the locking arm 9 is rotated only by the stepped portion 14 'approaching the projection 15. There is no.

In addition to the above-mentioned manual operation, the pin 10 is electrically rotated in response to a command signal from the driver to rotate the locking arm 9 clockwise (or vice versa) to obtain a lockable and lockable state. Is done. Referring to FIG.
An operating lever 17 having an arm portion 16 is fixed to the pin 10.
Wheel gears (18) rotatably supported on the housing are made to have opposite ends (19, 20) of a pair of raised protrusions facing a downward arm (16) of the tip of an 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, the groove 21 is narrowed in width by wall surfaces 22 and 23 which are opposed to each other. The coil spring 24 is put in the groove 21, and its end is brought into contact with the shoulders of the wall surfaces 22 and 23. Further, a protruding piece 25 protruding from the lower surface of the wheel gear 18 is located between the wall surfaces 22 and 23. As a result, for example, when the wheel gear 18 rotates clockwise as viewed in FIG. 10, the projecting piece 25 compresses the spring 24 while pushing the right end of the spring 24. At this time, the left end of the spring 24 is on the wall
It abuts the shoulders of 22, 23 and allows compression of the spring 24. In this rotation of the wheel gear 18, the end portion 19 of the convex portion 45 contacts the arm portion 16, the operation lever 17 and the pin 10 are rotated, and the locking arm 9 can be moved from the A position to the B position. To Rotation of the wheel gear 18 in the opposite direction is caused by the protrusion 25.
While the right end of the spring 24 is in contact with the shoulders of the wall surfaces 22 and 23, the spring 24 is compressed in the counterclockwise direction, the actuating lever 17 and the pin 10 are rotated by the end 20, and the locking arm 9 is moved to the B position. To A position. By using the annular groove 21 as described above, the total length of the spring 24 can be lengthened and sufficient bending can be secured.

The wheel gear 18 rotatably supported on the housing is
The rotation direction of the wheel gear 18 is controlled by meshing with a worm gear 27 directly connected to the electric motor 26 and controlling the energization of the motor 26. Generally, when the lead angle γ ₀ of the worm gear becomes larger than the friction angle φ, the rotation torque can be transmitted from the wheel gear 18 to the worm gear 27. Therefore, in this example, the advance angle is set to be equal to or greater than the friction angle (φ = 8.53 °) by utilizing the relationship of μ (friction coefficient) = tan φ. That is,
Worm gear 27 made of phosphor bronze and wheel gear 18 made of resin
Has a friction coefficient μ = 0.1 to 0.15 and a friction angle φ = 5.71 ° to 8.53 °, and the friction angle is set to 8.53 or more so that the wheel gear 18 can rotate the worm gear 27. The advance angle (γ ₀ ) of the worm gear 27 is selected by, for example, rotating the wheel gear 18 by the door lock operation by the driver using the electric motor 16 and immediately after the operation.
24 allows the wheel gear 18 to be returned to its original position and then manual operation. In other words,
It is possible to operate manually and then electrically, or manually after electrically. When operating manually, the operating lever 17 and wheel gear 18
Since the arm portion 16 is completely separated from the above, the arm portion 16 only idles between the both ends 19 and 20 of the pair of the convex portions 45, the motor portion is not dragged, it can be operated lightly, and the operation feeling is good.

As shown in FIG. 12, the pin 10 fixed to the actuating lever 17 actuated by the motor 26 in the sub housing 2'is
It has a stepped portion and a square portion 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 operating lever 13 on its outer peripheral surface. The square portion of the pin 10 protruding from the bearing portion 34 when the pin 10 is inserted into the bearing portion 34 is inserted into the hole 35 of the same shape of the locking arm 9 and fixed by caulking or the like. The locking arm 9 is seated on the top surface of the bearing portion 34. Since the bearing portion 34 for the key operation lever 13 is formed integrally with the housing 2, a separate bearing is not required, and the mounting portion of the locking arm 9 does not extend laterally outward.

As shown in FIGS. 12 and 13, the respective ends of the turnover spring 36 for holding the locking arm 9 in the locked and unlocked positions are provided with a recess 37 of the housing 2 near the bearing portion 34,
The hole 38 of the locking arm 9 that is almost opposite to this recess 37
And to lock. 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 allows the motor 26 to be downsized and allows the entire device to be made compact.

As has been 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 pole of the door lock operating part (not shown), and the pin 27 which can abut the pole moves the pole. It is moved to the latch release position, and thus the door lock operation portion is housed in the housing 2. The various levers and arms as described above are arranged on the outer surface of the housing 2. On the other hand, an actuator for rotating the pin 10, which is an output shaft including the motor 26 and the like, is housed in an extension portion of the housing 2 for the door lock operating portion. Further, as compared with a motor 26 and a wheel gear 18 which are arranged in a parallel relationship and which transmits a driving force to the output shaft 10 via a reduction mechanism such as a spur gear,
The electric motor 26 rotates the actuating lever 17 to move the locking arm 9 to the lock position (B) and the unlock position (B ′) shown in FIG. 1, but these positions (B,
B ') is provided with a stopper 39 for stopping the operating lever 17.
The function of the stopper 39 will be described with reference to FIG.
Although only one stopper 39 is shown in FIG. 14, the function of the other stopper is the same, so that the figure and its description are omitted.

To operate the electric motor 26, the wheel gear 18 is rotated via the worm 27, and the end 19 of the convex portion 45 causes the operating lever 17 to move.
Rotate with pin 10. At this time, the return spring 24 bends and stores energy for returning the wheel gear 18 to the neutral position. In this example, when the actuating lever 17 reaches the regular stop position 40, the actuating lever 17 and the stopper 39 come into contact with each other to prevent the movement of the actuating lever 17, but the stopper 39 is actuated by the rotational inertia force of the motor. The actuating lever 17 moves to the overtravel position 41 while elastically deforming. 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. The elastic force of the stopper 39 is applied when the electric motor 26 is turned off, that is, when the wheel gear is returned to the neutral position. It works to push the actuating lever 17 back together with the spring 24 to the regular locked and unlocked positions. The assisting force from the stopper 39 can reduce the biasing force of the spring 24 and the output of the electric motor 26 accordingly. The relationship between the wheel gear 18 and the motor reverse rotation torque is shown in FIG.

Fig. 12 shows the relationship between the pin 10 and the housing 2.
A more detailed description will be given with reference to FIG.

The pin 10, which is the output shaft fixed to the actuating lever 17, has a stepped structure including a large shaft diameter portion 40 and a small shaft diameter portion 41. On the other hand, the hole 32 of the housing 2'comprises a large opening 42 for receiving the large shaft diameter portion 40 and a small opening 43 for allowing the small shaft diameter portion 41. The locking arm 9 is fixed to a small shaft diameter portion 41 protruding from the housing 2 ', and the key operation lever 13 is rotatably supported by the bearing portion 34 of the housing 2'.

When mounting the pin 10 in the hole 32 of the housing 2 ', the O-ring 44 is fitted into the small shaft diameter portion 41 of the pin 10 so that the small shaft diameter portion 41 protrudes from the housing 2'from the inside of the housing 2'. Insert the output shaft 10 into the hole 32. When the output shaft 10 is inserted into the hole 32, the step portion of the hole 32 faces the step portion of the pin 10 via the O-ring 44. Thus, pin 10
It is possible to regulate the movement of the housing relative to the housing 2 '. This is useful to ensure correct movement of the actuating lever 17. Further, the O-ring 44 may be attached to the pin 10 and attached to the hole 32 of the housing 2 ', so that the assembling work is extremely easy.

In the illustrated example, in order to rotate the actuating lever 17,
As shown in Fig. 7, the wheel 18 has a semi-circular rising portion 45
However, instead of this, a pair of pins may be planted on the wheel 18. The ends 19 and 20 of the convex portion 45 are the operating lever 17
The arm 16 can be freely contacted. When the electric motor 26 is energized, the wheel 18 rotates via the worm 27. One end of the convex portion 45 comes into contact with the arm 16 in accordance with the rotation direction of the wheel gear 18, moves the operating lever 17 to the locked or unlocked position while compressing the return spring 24, and the pin 10 serving as the output shaft is moved. Move the link mechanism. Actuating lever 17
Occupy the locked or unlocked position and the motor 26 is de-energized, the release biasing force of the compressed return spring 24 causes the wheel 18, worm 27 and motor 26 to rotate in reverse, returning 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. When the electric motor 26 is energized, the gap 46 immediately sets the rotational speed of the motor to the rated value, and when the convex portion 45 comes into contact with the arm 16 of the operating lever 17, the inertia energy of the motor output shaft causes the inertia energy of the deceleration portion and the door. Increase the static friction of the lock mechanism etc. That is, when the convex portion 45 contacts the arm 16 of the actuating lever 17, the rotational inertia energy of the motor can be transmitted to the arm 16, so that the motor can be downsized.

Although the door lock device 1 has been described, the mounting portion of the door lock device 1 will be described with reference to FIG. The vehicle has a center pillar 49 between a front door 47 and a rear door 48, and a hinge 50 and a striker 51 for the rear door 48 are fixed to the center pillar 39. The striker 51 can be engaged with and disengaged from a ratchet (not shown) of the door lock device 1 when the front door 47 is opened and closed. on the other hand,
The windshield 52 of the front door 47 moves along the locus 53 along the center pillar 49 when moving up and down. Therefore, the door lock device 1 fixed to the front door 47 side
Avoid the trail 53 of windshield 52, windshield
It is necessary to prevent the interference between 52 and the door lock device 1. In order to avoid such interference, a recessed concave portion 54 is formed at the front edge of the center pillar 49, and a protruding portion 55 is formed at the rear edge portion of the front door 47, and the door is provided in the protruding portion 55. The lock device 1 is stored. That is, the door lock device 1 needs to have an external shape that can be accommodated in the limited space of the overhang portion 55. The shapes of the overhang portion 55 and the concave portion 54 are
It is designed not to interfere with the lower hinge 50 of the rear door 48. In this example, the rear edge of the front door 47 has a shape indicated by 113.

As is clear from FIG. 16, in this example, the main housing 2
In order to extend the lower part of the actuator and to dispose the electric actuator in this extension, the actuator is supported by the sub housing 2'and the sub housing 2'is fixed to the main housing 2. The main housing 2 accommodated in the overhanging portion 55 of the limited space described above has a shape extending forward at the lower portion thereof.

Referring to FIG. The mating surface 115 of the sub-housing 2'that fits the main housing 2 whose lower part is bent forward is provided with a mounting surface of the door lock device 1 in order to enhance the sealing performance therebetween.
It is a straight line inclined to 116. In order to further improve the sealing performance of the two housings 2 and 2 ', that is, to prevent the mating surfaces 115 of the two housings 2 and 2'from being displaced, as shown in FIG.
117 is provided, and the pair of hooks 117 are brought into contact with the lower end surface of the main housing 2. The abutment of the hook 117 with the lower end surface of the main housing 2 (see FIG. 20) prevents the displacement of both housings 2 and 2'when they are fastened to improve the sealing property, and further, the pin 10 serving as the output shaft It is possible to prevent misalignment with the pin receiving hole of the housing 2.

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-
The ring 119 is inserted and the O-ring 119 is bent by the mating surface 115 of the sub-housing 2'to secure the sealing pressure. The inner edge of the main housing 2 is a wall 120 extending upward,
Even if rainwater or dust passes through the O-ring 119,
The wall 120 prevents rainwater and dust from entering the housing 2. The wall 120 is effective for improving the sealing property even when the mating surfaces of the two housings 2 and 2'are bonded or welded together.

As described above, the shape of the housing is a substantially doglegged shape with the lower part projected toward the front of the vehicle. Therefore, as shown in FIG. 16, the actuating lever 17 has a shaft portion 121 fixed to the output shaft 10. Extends to the left of the page and locks and unlocks the housing 2
A step portion 125 for connecting the arm portion 124, which holds the contact element 123 to be detected in cooperation with the substrate 122 fixed to the substrate, and the arm portion 16, which is arranged so as to avoid interference with the shape of the lower portion of the housing, to be continuous.
Equipped with.

On the side of the shaft portion 121 that abuts on the bearing surface of the housing 2 ′,
The ring-shaped convex portion 126 is formed, which facilitates dimensional control in the thrust direction, reduces the contact surface with the housing 2 ′, reduces the rotational resistance, and forms the grease residue 127.

In addition, the arm portion 16 includes the convex portion 12 provided on the housing 2.
It is slidably supported by 8 to prevent the rotation resistance from increasing due to the entire contact between the arm and the housing.

The contact element 123 is composed of a fixed portion provided on the arm portion 124 of the actuating lever 17 and fixed to the protrusions 129 and 129 ', and contact portions 130 and 130' that slide on the substrate 122. A locking portion 131 is provided to prevent the arm from coming off the protrusion.

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

The substrate 122 is made of an insulating material such as epoxy resin, and a conducting portion made of copper or the like is provided in the passage portion of the contact portions 130 and 130 '.
131 and 131 'are arranged.

In the embodiment, the conductive portions 131 and 131 'are in contact with the contact portions 130 and 130', and the open state of the detection circuit is set to the unlocked state, and the closed state is set to the locked state.

In this way, since the switch portion is arranged on the actuating lever 17 directly connected to the locking lever 9 for switching between locking and unlocking, the position detection accuracy is improved, and further, the substrate 122 fixed to the housing 2 is provided. Arm part 1 of actuating lever 17
Since the arrangement is made so as not to overlap the projections 129 for fixing the contact pieces 123 of 24, the substrate and the arm portion can be brought as close to each other as possible, and the height of the driving portion can be reduced.

Please refer to FIG. 22 and FIG. Clip to door panel 187 1
If a seal 189 made of rubber or the like that is mounted at 88 and seals between the door and the body is arranged so as to pass over the actuator portion of the door lock, the above-mentioned clip 18
Interference with the tip 190 of the 8 becomes a problem.

In the present embodiment, paying attention to the void created in the upper part of the housing of the motor of the housing 2, the recessed portion 191 that is recessed as much as possible is provided.
The clearance between the tip 190 of the clip 188 is secured.

In this way, the actuator part shaped like a dogleg,
Furthermore, by providing a recess for avoiding interference with the tip of the clip, it is possible to reduce the substantially required space between the door panel 113 and the ascending / descending path 114 of the door glass in FIG. It is possible to obtain a compact door lock with a high degree of freedom.

In the embodiment shown in FIG. 22, the screw 192 is used to connect the housings 2 and 2 '.

As shown in FIGS. 17, 24, and 25, the housing 2 '
Has a hole 193 larger than the outer diameter of the screw 192 through which the screw 192 penetrates, and the housing 2 has a fastening hole 194 slightly smaller than the outer diameter of the screw 192.

Referring to FIG. In order to prevent the relationship between the housings 2 and 2'from being displaced by fastening, the holes of the housing 2'arranged diagonally are made holes 195 slightly smaller than the outer diameter of the screw 192, so that the screw 192 is automatically tightened when tightened. The screw shaft center and the hole center are made to coincide with each other.

As described above, the low-cost and space-saving centering structure can reduce the output loss at the bearing portion of the pin 10 caused by the displacement between the housings 2 and 2 ', and thus reduce the motor output. The motor can be downsized and smooth and quiet operation can be obtained.

Please refer to FIG. 17, FIG. 24 and FIG.

A stopper 197 is provided at a position facing the stopper 39 of the housing 2'to prevent the stopper 39 held by the stopper holding portion 196 of the housing 2 from coming off.

In this way, by providing the retaining member 197, the impact load including the rotational inertia load of the motor at the locked and unlocked positions is applied to the stopper 39 via the actuating lever to cause elastic deformation, and the stopper holding portion described above is provided. Even if you try to get out of the 196, it will be blocked by the stopper 197, so you can guarantee the retention of the stopper 39 against repeated loads, and for a long time,
Can maintain stable performance.

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

Air bleeding in the housing will be described with reference to FIGS. 16 and 28. Lower end of housing 2 (left side of paper)
Has an air hole 107 formed in cooperation with the housing 2 '.
Is provided, and due to changes in the environment, such as changes in temperature,
The inside of the housing has a negative pressure so that rainwater etc. adhering to the outer circumference of the housing will not be sucked into the inside.

The shape of the air hole 107 is such that a wall 109 facing the opening 108 is provided, and the wall 109 and the wall 110 facing each other make the air hole substantially U-shaped.
The hole is formed in a V shape, and the size of the hole is formed by the side walls 111 and 112 into a substantially square shape. Therefore, the opening 108
Even if water droplets such as rainwater adhere to the vicinity of or there is dust or the like, the two walls 109 and 110 prevent the water from entering the housing 2.

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

A void 1 created between the door lock plate 178 that abuts the door lock mounting surface 116 of the door panel and the housing 2.
A meshing mechanism that holds the door closed state of a known door lock is housed in 79.

A groove 180 formed between the plate 178 and the above-mentioned plate 178 is provided in the lower part of the void 179 for draining rainwater and the like, and is extended as much as possible to a position below the plate 178.

A water channel 182 is formed in the lower portion of the groove 180 in a state where the bearing portion 181 of the pin 10 is moved to the door panel 113 side as much as possible, and the groove 180 is substantially terminated by the wall 183.

In this way, by providing the wall 183 that limits the groove 180, the thickness of the door lock actuator portion in the vehicle longitudinal direction can be reduced, and a clearance between the door lock and the up-and-down trajectory 114 of the door glass can be secured.
The door lock device can be placed above the door to improve the strength of the upper part of the door against collisions, or
Since it can be placed behind the door from the ascending / descending trajectory, the door glass area can be increased and the design flexibility can be increased.

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

The wheel gear 18 is rotatably pivotally mounted on a shaft 100 that is inserted in the housing 2 ', and its movement in the slip-off direction is restricted by a washer 101 that is swaged at the tip of the shaft 100.

A washer 102 is inserted between the wheel gear 18 and the housing 2'to reduce the resistance during rotation to prevent contact between the resins.

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

In the portion of the shaft 100 that is inserted into the housing 2 ', the strength against bending and rotation of the shaft 100 caused by the engagement of the worm gear 27 and the wheel gear 18 is increased, and the holding strength in the thrust direction is improved. In order to make it so that the tip of the shaft 100 and the other end 105 for receiving the washer 101 at the time of crimping are projected to the outside from the surface of the housing 2 ', a path for inserting rainwater or the like through the gap is lengthened, A brim portion 106 is provided to prevent intrusion.

FIG. 17 is a view seen from the inside of the housing 2 ', showing the positional relationship among the pin 10, the operating lever 17, the wheel gear 18, the motor 26, and the worm gear 27. As is clear from FIG.
The pin 10 is supported by the bearing portion 34, the wheel gear 18 is supported by the inserted shaft 100, and the worm gear 27 and the motor 26 are supported by the support portions 132, 133, 134 provided in the housing 2 '. The movement of the motor itself in the rotation direction is prevented by the walls 135 and 136.

In this way, the positional relationship of the drive transmission system, especially the wheel gear 18
Of the worm gear 27 and the auxiliary housing 2 '
Since it is determined by only the manufacturing error such as the distance between the pitches of the gears can be minimized, smooth power transmission can be achieved, and the motor outlet loss can be reduced, which leads to downsizing.

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

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

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

To the motor shaft 140, a commutator portion 143 that receives electric power from the outside and a core 145 that holds the winding 144 are fixed.

Further, a collar 146 is arranged between the core 145 to prevent interference between the winding 144 and the case 137. Magnet
14g is fixed to the case 137.

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

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

By the support portion 133 that supports the bearing portion 137 ′ of the case 137 and the support portion 132 that supports the bearing portion 138 ′ of the case 138,
The position of the motor in the thrust direction and the positional relationship with the shaft 100 that pivotally supports the wheel gear 18 are determined.

Next, the worm gear 27 has a spherically shaped shaft 15
The support portion 134 that supports 2 will be described.

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

In addition, a load is applied to the motor shaft 140 in the direction of entering the motor case side, and one end 147 of the motor shaft is thrust plate 149.
When it comes into contact with and rotates, since it comes into contact with the spherical surface, it has a small rotational resistance and can rotate with a light torque.

On the contrary, when a load is applied in the direction of pulling out the motor shaft, the end surface of the collar 146 and the end surface of the bearing 141 come into contact with each other, the rotation resistance is large, and a large torque is required to rotate the motor shaft.

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

Further, when the power supply is stopped after driving the motor, the return spring 24 drives the wheel gear 18 to
With the structure that returns to the neutral position while rotating 27, the rotation resistance of the motor shaft is large and the output of the return spring must be increased, and the output of the motor must be increased accordingly. As described above, in order to prevent the contact between the collar 146 and the bearing 141, which causes various output losses, a motor shaft length 154 is provided between the shaft portion 152 having a spherical end of the worm gear 27 and the support portion 134. A gap 156 between the collar 146 and a gap 153 smaller than the gap 153 between the end faces of the bearing 141 is set while absorbing a manufacturing error with the length 155 of the support portion 134 to the thrust load receiving surface.

Therefore, even if the motor shaft 140 moves in the direction of pulling out from the case, the spherical tip of the shaft portion 152 of the worm gear 27 and the support portion 134 come into contact with each other, so that the collar 146 and the end surfaces of the bearing 141 do not come into contact with each other. It is possible to prevent an increase in rotation resistance, prevent loss of motor output, and reduce the size of the motor.

The manufacturing error between the support parts 132 and 133 is set in the direction in which the motor case and the gap are generated because the support part 133 cannot be completely absorbed by the elastic deformation of the support part 133.
This is performed so that 138 and the supporting portion 132 contact each other.

Further, even in the radial direction of the shaft portion 152 of the worm gear 27, the support portion 1
34 and a minute gap are set, for example, when the operating lever is stopped at the locked or unlocked position and the inter-pitch distance is about to increase due to the meshing reaction force with the wheel gear 18, it comes into contact. .

The power supply to the motor is cut off, and the return spring 24
When the wheel gear 18 is driven and the worm gear 27 is rotated to return to the neutral position, the contact between the support portion 134 and the shaft portion 152 is released, so there is no loss of the return spring force at this portion, so The return spring force is also small enough that the motor can be downsized. In addition, it is the supports 132 and 1 that determine the normal motor axis.
33, the manufacturing error can be easily absorbed, and an inexpensive housing can be obtained.

Next, the housing 2 is provided with the following supporting portions, respectively. That is, as shown in FIG. 31, the tip of the worm gear 152
A support portion 157 is provided that abuts when is displaced.

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

As shown in FIG. 33, an elastic body 159 such as a sponge is attached to the housing 2 side of the motor case 137 supported by the housing 2 '.
However, if the dimension between the housing 2'and the housing 2 can be increased, the supporting portions 132 and 1
If the dimension 160 between the motor and 33 is large and there is a gap between the motor case and the motor case, the motor case may open due to door opening / closing, vibration during running, or worm mesh reaction force when the motor is driven. It prevents movement and noise.

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

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

FIG. 35 shows a standard meshing state of the worm gear 27 and the wheel gear 18. Reference numeral 162 represents the teeth of the wheel gear, 163 represents the teeth of the worm gear, and 164 represents the backlash at the standard time.
The wheel gear 18 has a complicated shape as shown in FIGS. 16 and 17, and is therefore made of resin. In such a complicated shape and inconsistent wall thickness, distortion of the outer diameter shape due to molding is difficult to resist, and when the tooth width is increased, backlash is reduced and smooth tooth engagement operation is not possible.
When a sink mark occurs, a load is applied to the tooth tip, resulting in a decrease in strength.

Generally, in order to increase the backlash, the method of making the distance between pitches larger than the standard value, Fig. 36 is taken, but a speed reducer using a small gear, for example, module 0.6 (tooth tooth 1.3
In the case of 5 mm), the distance between pitches can be increased only slightly, and the required amount of backlash cannot be obtained. In addition, since the load is further applied to the tooth tips, particularly in the case of driving a lever or the like that comes into contact with a fixed object and is operationally restrained after a predetermined operation, the motor rotation is suddenly stopped during the stop, so that the motor The impact load including the rotational inertia energy acts, and the teeth themselves are damaged.

In the embodiment of the present invention shown in FIG. 37, a resin wheel gear is used.
The tooth profile of 18 and the distance between pitches are standard, and the backlash is increased by laterally shifting the teeth of the phosphor bronze worm gear 27, which has a relatively large strength. Reference numeral 165 denotes a tooth of the worm gear whose tooth width has become smaller due to lateral dislocation, and 166 denotes backlash increased due to lateral dislocation. In this way, since the distance between the pitches is standard, it is possible to prevent the tooth tip from hitting, no loss in strength, and the tooth distortion of the wheel gear can be absorbed.

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

FIG. 38 shows the protrusion 45 of the wheel gear 18 meshed with the worm gear 27 and the arm of the operating lever 17 driven by the motor.
16 is in contact with the lever 17, and the lever 17 is in the unlocked position in contact with the stopper 39. FIG. 39 shows a state in which it is similarly moved to the lock position.

In FIG. 38, an arrow 167 indicates a driving force given to the wheel gear 18 by the worm gear 27. Arrow 168 indicates stopper 3
Reaction force from 9 to actuating lever 17, 169 from arm 16 to protrusion 45
Shows the reaction force to the end of. FIG. 40 is a view from H of FIG. 38, and the wheel gear 18 is provided with a tooth 170 on the upper right side in the drawing. The driving force 167 given by the worm gear 27 is
In the case of the tooth streak as shown in the drawing, the component force 171 that is directed upward in the drawing is generated by the inclination of the tooth 170. FIG. 41 is a view as seen from J in FIG. 38. The aforementioned component force 171 causes the resin wheel gear to elastically deform in the direction in which the meshing with the worm gear becomes shallow, in the counterclockwise direction on the paper surface, or in the shaft 100. Although the insert portion is elastically deformed, the reaction force 169 acting on the convex portion 45 that generates a reaction force in the clockwise direction on the paper surface prevents the engagement of the wheel gear and the worm gear from becoming shallow.

In FIG. 39, 172 is a wheel gear 18 rather than a worm gear 27.
The reference numeral 173 represents a reaction force from the stopper 39 to the actuating lever 17, and the reference numeral 174 represents a reaction force from the arm 16 to the convex portion 45.

FIG. 42 is a view as seen from K in FIG. 39, and the driving force 172 applied from the worm gear 27 generates a component force 175 that moves downward in the drawing.

FIG. 43 is an L view of FIG. 39, and the aforementioned component force 175 elastically deforms the wheel gear or the insert portion of the shaft 100 in the direction in which the engagement with the worm gear becomes deeper and in the clockwise direction on the paper surface. .

When the operating lever 17 is stopped by the stopper 39, the contact point between the convex portion 45 of the wheel gear 18 and the arm 16 is the worm gear 27.
Since it is located in the vicinity of the line connecting the shaft 100 and the shaft 100, the reaction force 174 does not generate a drag force effective in preventing the meshing from becoming shallow. However, due to the action of the component force 175,
The shallow meshing is prevented.

FIGS. 44 and 45 show a case in which the upper left tooth 176 is provided on the paper in the tooth streak direction. Driving force given by worm gear 27
172 generates a component force 177 that is directed upward in the plane of the drawing. Thus, the upward component force reduces the meshing relationship between the worm gear and the wheel gear, but the reaction force 174 acting on the convex portion 45 as described above is effective in preventing the meshing from becoming shallow. Since no drag is generated, for example, the tooth tips of the resin-made wheel gear may be lost, or the tooth tips of the gears may run up and become immobile.

As in the embodiment shown in FIGS. 40 and 42, the stopper position of the operating lever 17 is near the line connecting the worm gear 27 and the shaft 100, and the contact point between the convex portion 45 of the wheel gear 18 and the arm 16 is located at the position. In this case, the component force generated by the driving force from the worm gear determines the tooth streak in the direction in which the meshing does not become shallow, so it is possible to obtain freedom in the arrangement of the operating lever, wheel gear, worm gear, etc. A power actuator for a door lock can be realized.

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

Although the operational relationship between the convex portion 45 and the arm 16 is described in FIG. 17, in order to improve the lever ratio, the contact point of the convex portion 45 of the wheel gear 18 with the arm 16 should be as much as possible. Is located closer to the rotation center side of, and the contact point with the convex portion 45 of the arm 16 is
As far as possible, it is preferable that the lever 17 is arranged at a position far from the rotation center of the lever 17. Due to the tapering of the convex portion 45 of the wheel gear 18 that runs idle between the gaps 46, the tip portion 225 rounded to the tip and the substantially C-shaped cam surface 226 that spreads toward the tip of the arm 16 come into contact with each other. . The substantially C-shaped cam surface 226 of the arm 16 is effective in disposing the contact point of the tip end portion 25 of the convex portion 45 at a position as far as possible from the rotation center of the lever 17.

The cam surface 226 having the substantially C-shape changes from the middle to the cam surface 227 which is formed thin toward the tip. The cam surface 227 and the tip end portion 225 start to come into contact with each other at a substantially intermediate position of the operation of the lever 17, and the cam surface 228 formed continuously with the tip end portion 225 gradually.
In the stop position where the arm 17 is stopped by the stopper 39, the cam surface 228 and the arm 1 are completely moved.
It is in contact with the cam surface 227 of 6.

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

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

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

At the locked and unlocked positions, the motor is driven while the stopper 39 is elastically deformed by being further loaded in the direction in which it operates, the gap 230 disappears, and the arm 16 enters the rotation path of the wheel gear tip 225. When the switch is operated, the tip portion 225 and the arm 16 interfere with each other, do not operate normally, and damage or damage the respective contact surfaces.

In the embodiment, since the arm 216 is provided with the extension portion 229, even if an overload is applied, the arm gear does not enter the operation locus of the wheel gear, and the normal operation by the operation of the switch can be secured.

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

The switch for detecting that the key is operated to be locked or unlocked will be described in detail. Please refer to FIG. 22, 47, 23, 48, 49. The detection switch 205 is rotatably supported by the main body 207 and the main body 207, which is fixed to the housing 2 ′ by a screen 206 or the like, and has one end 208 of the hole 2 of the key operation lever 13.
Inserted in 09, it consists of a movable part 210 that operates in conjunction with the rotation operation of the key operation lever 13, has the same contact part and conduction part as shown in FIG. 21 inside, and locks and unlocks positions. To detect.

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

The housing 2'has a space 212 for accommodating the main body 207.
Is provided and a hole 213 into which the screw 206 is tightened is provided.
Is set.

The substantially U-shaped groove 214 is formed by walls 215 and 216 and serves as a passage for the above-mentioned wire harness 211 and continues to a passage 217 provided on the side wall. A clip 218 is locked to the wall 215 described above, and the upper end piece 219 of the clip 218 causes the groove 214 to
The opening of the wire harness 211 is closed to prevent the wire harness 211 from jumping out of the groove 214. Incidentally, FIG. 60 is a view N of FIG. 47.
FIG.

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

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 it is possible to give a sufficient clearance to the glass ascending / descending path 114 in FIG. It is possible to obtain a compact door lock that can reduce the required space and has a high degree of freedom in placement on the vehicle.

There is enough clearance with the door glass up / down trajectory 114,
In the case where the wire harness 211 can pass through on the side surface of the housing as well, the wire harness 211 is locked to the hook 231 provided on the housing 2 shown in FIGS. It can be prevented from freely floating, and the number of parts and assembling workability are lower than those using the clamp 186 shown in FIGS.

Please refer to FIG. 47, FIG. 23 and FIG. The rotation operation of the key operation lever 13 is transmitted to the projection 15 of the locking arm 9 from the projection 14 and the step 14 ', and the locking arm 9 is rotated.

The switch 205 needs to be arranged closer to the door lock in order to secure sufficient clearance with respect to the glass elevating path 114 of FIG.

As shown in FIG. 23, the protrusion 15 is bent toward the housing 2 ′ because it overlaps with the switch 205 in the vicinity of the rotation centers of the key operation lever 13 and the locking arm 9, so that the protrusion 15 and the housing 2 are not bent. In order to secure the clearance between ‘
A recess 220 is provided during the operating range of the protrusion 15.

With such an arrangement, the switch 205 can be moved closer to the door lock side.

Further, a recess 221 is provided on the bottom surface of the movable portion 210 of the switch 205,
By avoiding the interference between the locking arm 9 of the output shaft 10 and the caulking portion 222, the switch 205 can be moved closer to the housing side.

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

Boss portion 2 extending to the mounting surface side of housing 2'of main body portion 207
23, and the aforementioned boss portion 223 provided in the housing 2 ′ is inserted into the hole 224 for determining the position of the switch 205.
Is available.

In this way, the switch 205 is formed by the boss portion 223 and the hole 224.
Is one end 208 of the movable part 210 and the hole 209 of the key operation lever 13.
And are mounted in the correct relationship to detect lock and unlock accurately.

Please refer to FIG. 29 and FIG. 184 is a motor 26 and a substrate 122
Is a wire harness wired to the conducting portion of the housing 2, and is fixed to the housing by a clamp 186 penetrating a clamp hole 185 provided in the housing 2, 2 '. Therefore, when you install it on the vehicle, pull the connector (not shown) at the end of the wire harness to connect it to the mating connector, or if you hold the connector and hang the door lock body, this pull The load is the above-mentioned clamp
Since it does not reach the portion accommodated in the housing and accommodated in the housing 186, immobility due to disconnection can be prevented without damaging the coupling portion with the motor or the coupling portion with the conductive portion of the substrate.

FIG. 52 shows an O-ring 1 inserted along the groove 118 of FIG.
19 includes a harness holding portion 198 through which a wire harness disposed in a conductive portion of a motor and a substrate penetrates, and a grip portion 199 for improving workability when inserting into the groove 118.

FIG. 53 shows the details of the grip portion 199 in which a protrusion 200 is provided on the outer circumference, and the diameter is set to be slightly larger than the width of the groove 118. The groove 118 is formed to reduce the outer shape of the drive unit.
As shown in FIG. 24, it has a serpentine shape with few straight parts, and when the O-ring 119 is inserted and installed in the groove 118, the O-ring itself will protrude from the groove due to the restoring force to return to the straight shape. The workability was very poor.

In the embodiment, by providing the grip 199 set in the outer diameter shape larger than the groove width in several places, it is possible to prevent the phenomenon of protruding from the groove, and the insertion work is greatly improved,
The housing 2 and 2'will not be pinched at a position other than a predetermined position, the sealing performance will be impaired, and water, dust and the like will not enter the inside of the housing to reduce the function of the drive unit.

Fig. 54 is an N view of Fig. 52, which is provided with a hole 202 through which the wire harness passes.

Fig. 55 is a P-P cross section of Fig. 54, and the convex portion 203 having a diameter smaller than the outer diameter of the harness is provided inside the hole 202.
Is provided.

FIG. 56 shows a state in which the harness holding portion 198 is attached to the housings 2 and 2 ', and the housings 2 and 2'are provided with the convex portions 204 and 204'. There is.

Intrusion of rainwater and dust is prevented by the convex portion 203 between the harness and the hole 202, and by the convex portions 204, 204 'between the harness holding portion 198 and the housings 2, 2'.

Furthermore, the convex portion 203 has a function of limiting the movement of the harness, and prevents displacement when a load is applied to the tip of the harness.

(Effect) The present application is an actuator for locking and unlocking a door lock, which comprises one housing through which the output shaft penetrates and another housing which cooperates with this housing to enclose the actuator mechanism. The output shaft, the gear shaft that transmits the torque of the motor to the output shaft, and the positional relationship between the motor shaft are substantially determined, so that the dimensional accuracy between each element of the power transmission path is ensured and the power transmission is ensured. It is possible to improve efficiency and productivity.

Further, in the present application, a clearance is usually set in the shaft radial direction, and the shaft is supported so as not to cause disengagement only when the motor shaft is elastically deformed during overload, so there is no bearing loss in normal operation. , Normally, a gap smaller than the amount of backlash in the longitudinal direction of the shaft is also set, so even if the shaft operates in a direction that pops out of the main body, it does not serve as a stopper inside the motor, so rotation due to shaft thrust load The increase in resistance can be prevented, a smaller motor can be adopted, special strict manufacturing precision is not required, and the weight and cost can be reduced. In particular, in the structure in which the lead angle is made larger than the friction angle and the wheel is reversed from the wheel side, there is no bearing loss, so the return spring force can be reduced, and the output performance can be improved accordingly.

[Brief description of drawings]

FIG. 1 is a front view showing this example, FIG. 2 is a partial front view showing a state in which an open lever is operating a release lever, and FIGS. 3 and 4 are partial front views showing an idle state of a locking mechanism. 5 and 6 are partial front views showing the keyless lock mechanism, FIGS. 7 and 8 are partial front views showing the self-cancelling mechanism, FIG. 9 is an exploded view of the actuator portion, and FIG. 10 is Fig. 11 is 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 mounting portion of the output shaft, Fig. 13 is a side view showing the mounting of the turnover spring, and Fig. 14 is an operating lever. And FIG. 15 is a plan view 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 actuator section. 18 Figure shows the storage part of the door lock device Front view, FIG. 19 is a front view of the door lock device, FIG. 20 is a partial cross-sectional view showing the O-rings of both housings, FIG. 21 is an enlarged partial plan view of the switch portion, and FIG. 22 (a) is a door. A front view of the locking device, FIG. 22 (b) is a partial perspective view of the switch part, FIG. 23 is a side sectional view of the actuator part, FIG. 24 is a plan view of the actuator part, and FIG. 25 is a screw fastening part. Partial cross section, No. 26
Fig. 27 is a sectional view of another part of the screw fastening part, Fig. 27 is a sectional view showing a state where the stopper is housed, Fig. 28 is a view seen from the arrow S-S in Fig. 16, and Fig. 29 is a door lock device. FIG. 30 is a plan view seen from the vehicle mounting surface side, FIG. 30 is a plan view showing a support structure for a motor and a worm gear shaft, and FIG. 31 is an arrow DD in FIG.
32 is a sectional view taken along line EE of FIG. 20, FIG. 33 is a sectional view taken along line FF of FIG. 20,
FIG. 34 is a sectional view taken along the line GG in FIG. 20, FIG. 35 is a partial plan view showing the engagement between the worm gear and the wheel gear, and FIG. 36 shows a large pitch between both gears. Partial plan view, FIG. 37 is a partial plan view showing a state in which the worm gear is laterally displaced, FIGS. 38 and 39 are plan views showing reaction forces acting on respective parts, and FIG. 40 is an arrow view of FIG. 38. The figure which shows the component force when it sees from H direction, FIG. 41 shows the component force which it sees from the arrow J direction of FIG. 38, FIG. 42 shows the component force which it sees from the arrow K direction of FIG. Fig. 43 is a diagram showing the component force as seen from the direction of arrow L in Fig. 39, Fig. 44 is a diagram seen from the K direction in Fig. 39 when the tooth streaks are reversed, and Fig. 45 is a tooth streak. FIG. 39 is a plan view showing the relationship between the operating lever and the wheel when viewed in the direction L in FIG. 39 when it is reversed, FIG. 47 is a plan view of the housing portion, and FIG. 48 is a wire harness clip. Disconnection Fig. 49 is a sectional view showing a passage of a wire harness, Fig. 50 is a sectional view of a mounting part of a switch part, Fig. 51 is a sectional view of a clamp part of a wire harness, and Fig. 52 is a whole O-ring. Fig. 53 is a sectional view taken along the line Q-Q in Fig. 52, Fig. 54 is a view seen from an arrow N in Fig. 52, Fig. 55 is a view seen from an arrow P in Fig. 54, and Fig. 56 is Fig. 57 is a sectional view of the wire harness holding portion, Fig. 57 is a sectional view of the wire harness clamp portion, 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. 60 is a perspective view. It is the figure seen from the arrow N of FIG. In the figure: 1 ... Door lock device, 2, 2 '... Housing,
3 ... Release lever, 5 ... Open lever, 8 ...
Locking button, 9 ... Locking arm, 10 ... pin, 13 ... Key operating lever, 15 ... Projection part, 17 ... Actuating lever, 24 ... Return spring, 26 ... Motor, 27 ...
… Worm gear, 34 …… Bearing, 36 …… Turnover switch, 39 …… Stopper, 159 …… Elastic material, 166 …… Backlash, 225 …… Tip part, 226, 227, 228 …… Cam surface.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Soichiro Okudaira 1 Toyota-cho, Toyota-shi, Aichi Toyota Motor Co., Ltd. Examiner Yasuhito Tsujino (56) Reference JP-A-1-250582 (JP, A) Kai 63-93980 (JP, A)

Claims (1)

[Claims] 1. A door lock device in which an actuator portion is housed in a lower portion of a main housing which houses a meshing portion for a door lock, and an electric motor which constitutes the actuator portion in a sub-housing fixed to a lower portion of the main housing. A motor, a worm gear fixed to the motor shaft of the electric motor, a wheel gear that meshes with the worm gear, and an operating lever that is engageable with the protrusion of the wheel gear are supported, and the end of the motor shaft is radially and A gap is provided between the core that supports the electric motor windings and has a gap in the axial direction and a bearing that supports the motor shaft adjacent to the core, and the gap between the former and the gap between the latter is Door lock device that is smaller than the space.