JPH06307502A - Motor device with worm gear - Google Patents

Abstract

PURPOSE:To improve the durability of a gear part by making an action for restraining the thrust displacement of a worm wheel generated by the impact force of a motor device provided with a worm gear or placing both directional changes of a meshed area by the displacement in the increasing direction. CONSTITUTION:A holder 20 is installed on the outer peripheral upper edge of a worm wheel 12 so as to be arranged to prevent any relative displacement in an axial direction by means of the stop ring 17 of a boss 7 and installed in parallel with a cover 18 at a minute clearance thereto and the maximum outer diameter of a part having the minute clearance is made a gear effective diameter or less of the worm wheel 12.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a motor device with a worm gear used for driving a window opening / closing device of a vehicle, for example.

[0002]

2. Description of the Related Art Generally, there are two types of power window motors for automobiles, one of which is mounted inside a door and which opens and closes a window through a gear or the like so that only an operation switch is mounted on a trim side of a vehicle interior. There is a type in which a manual opening / closing handle provided on the side is removed and a drive motor is attached to the handle shaft. The latter is in great demand for aftermarkets or options, which will be explained with reference to FIGS. 6 and 7. FIG. 6 is a view when it is mounted on a door, and FIG. 7 is a sectional view taken along line VII-VII of FIG.

In the drawing, 1 is a power window main body, 2
Is a bracket for attaching the power window body 1 to the door inner side panel 3, which is fixed by attaching screws 4 and 5. A window driving handle shaft 6 is inserted into a boss hole 7a formed in the boss 7 of the power window body 1. The handle shaft side serration 6a and the boss side serration 7 are arranged so that the boss hole 7a and the handle shaft 6 rotate in the same direction.
It matches with b. The handle shaft 6 is configured to open and close the window by rotation of the handle shaft 6 via a gear, an arm mechanism, and the like provided inside the door.

FIG. 8 is a top view showing a state in which the cover is removed from the conventional power window body, and FIG. 9 is a line IX-- in FIG.
FIG. 10 is a sectional view of IX, and FIG. 10 is an exploded perspective view thereof. In the figure, reference numeral 8 is a motor body, which is configured to convert an applied power into a rotation output and transmit the rotation output to the worm shaft 9.
The motor body 8 can change its rotation direction depending on the direction of applied voltage. Reference numeral 10 denotes a gear housing which fixes the motor body 8 with screws 11 and rotatably holds a worm shaft 9 output from the motor body 8.

The worm wheel 12 has a boss 7 at the center.
Has a hole 12a into which the worm shaft 12 is inserted, and is rotatably held in a bearing hole 10a provided in the gear housing 10 by a convex portion 12b that is concentric with the hole 12a and extends in the axial direction. And are arranged so as to mesh with each other at right angles.

A cushion 15 formed by vulcanizing and adhering the plate A13 and the plate B14 is arranged on the worm wheel 12. The plate A13 is arranged so that the convex portion 13a on the outer periphery thereof is inserted into the concave portion 12c of the worm wheel 12 and is rotated by the convex portion 12b. The plate B14 has a substantially triangular shape in which three points of the inner circumference circle are straight lines, and is fitted to a substantially triangular portion 7c in which the three points of the tip circle of the boss 7 mounted at the center of the worm wheel 12 are straight lines. Are configured to rotate the same.

The boss 7 is inserted into the center of the worm wheel 12 and the cushion 15 mounted on the gear housing 10 via a gap adjusting spacer A16, and is axially moved by a ring 17 mounted on a recess 7d provided at the tip. The degree of freedom is regulated. In addition, a boss hole 7a for inserting a handle shaft is provided in the center, and the serration 7 is provided inside.
b is provided. The handle shaft can be inserted into the boss hole 7a from both directions of the motor main body 8 so that the boss hole 7a can be shared by the left and right doors. Cover 18
Is fixed to the gear housing 10 with screws 19 to protect internal parts and prevent the grease applied to the gear system from scattering.

Next, the operation will be described. When the window of the automobile is opened, a switch provided on the door lining portion is pushed in the opening direction, whereby a voltage in the opening direction is applied to the motor body 8 to rotate in the opening direction. This rotational force is directly transmitted to the worm shaft 9, and the worm wheel 12 orthogonal to this is applied.
Be transmitted to. At this time, a reduction mechanism in which the worm wheel 12 is fed by one tooth per rotation of the worm shaft 9 increases the rotational torque and decreases the rotational speed.

The rotational force transmitted to the worm wheel 12 is transmitted to the plate A 13 and then transmitted from the plate B 14 to the boss 7 via the cushion 15. The rotational force transmitted from the serration 7b provided on the inner circumference of the boss 7 to the handle shaft side serration 6a is transmitted in the opening direction of the window via a gear, an arm mechanism and the like provided inside the door. The window operated in the opening direction is forcibly stopped from moving by a lower limit stopper provided inside the door. At that time, the inertial force of the rotating body inside the motor body 8 is absorbed by the cushion 15 bending in the rotating direction, and the impact force on the worm gear 9 is relieved.

When the window is closed, a switch provided on the door lining portion is pushed in the closing direction, so that a voltage in the closing direction is applied to the motor body 8 to rotate the motor body 8 in the closing direction. The motion transmission is the same as when it is opened, and only the rotation direction is different.

[0011]

Since the conventional motor device with a worm gear is constructed as described above, the worm wheel 12 is wormed by the impact force generated when the window is forcibly stopped at the upper limit and the lower limit. Radial radial crushing load is applied by the tooth profile pressure angle of the shaft 9, and thrust load is generated by the gear feed angle. As a result, the engagement depth is reduced due to the radial displacement of the worm wheel and the thrust displacement, and in the worst case, the gear is ridden or locked due to the engagement. Normally, the impact force is absorbed and relaxed by the deflection of the cushion 15, but the cushion dimension must be increased in order to have sufficient performance, and it is configured to have the minimum performance due to the balance of performance and dimensions. Therefore, it is necessary to improve the durability by using a structure other than the cushion.

The change in meshing depth due to thrust displacement is
As shown in FIGS. 11 to 14, an increase and a decrease occur depending on the rotation direction. FIG. 11 is a diagram showing meshing dimensions in a steady state, and FIG. 12 is a diagram seen from the direction of arrow XII in FIG. FIG. 13 is a diagram showing the displacement when the worm shaft 9 is forcibly stopped during clockwise rotation, and the worm wheel 12 is displaced in the direction opposite to the bearing portion of the worm wheel 12 by the feed angle of the gear. At that time,
Since the worm wheel 12 is offset by L from the center of the worm shaft 9 and rotates about a fulcrum C separated by M, its meshing area S ₂ is smaller than the meshing area S ₁ in the steady state.

FIG. 14 is a diagram showing the displacement when the worm shaft 9 is forcibly stopped during counterclockwise rotation. The worm wheel 12 is displaced in the direction of the bearing portion of the worm wheel 12 depending on the feed angle of the gear. To be made. At that time, the worm wheel 12 is offset from the center of the worm gear 9 by L and rotates about the fulcrum G separated by N, so that the meshing area S ₃ thereof increases compared with the meshing area S ₁ in the steady state.

Due to this phenomenon, the worm wheel 12
Since the material of is often resin, the strength is most reduced when the worm shaft 9 is rotated clockwise and forcibly stopped at a high temperature where the strength is significantly reduced.
Locking due to gear riding or biting is most likely to occur. In the case of this example, the meshing area decreases in the clockwise rotation due to the gear feed angle direction, the worm gear arrangement direction, and the like, but depending on the specifications, there may be a case where the rotation is opposite.

In particular, in the case of a type in which a manual opening / closing handle provided on the trim side of the vehicle interior of the door is removed and a drive motor is mounted on the handle shaft, it is necessary to secure a space for inserting the handle shaft in the center. Therefore, the bearing diameter of the worm wheel 12 needs to be relatively large,
In addition, the thickness of the main body must be as thin as possible because it is mounted on the trim side of the passenger compartment. Therefore, the bearing structure has a large diameter and a short bearing length, and displacement (tilt) of the worm wheel 12 in the thrust direction is likely to occur.

The present invention has been made in order to solve the above-mentioned problems, and the thrust displacement of the worm wheel due to the impact force generated when the motor is stopped or the like is pressed in both directions, so that the meshing area of the gear is reduced. An object of the present invention is to obtain a motor device with a worm gear that can increase the cushion durability and improve the cushion durability and further reduce the contact noise.

[0017]

In a motor device with a worm gear according to a first aspect of the present invention, a holder is arranged so as to prevent relative displacement in the axial direction of a worm wheel and a boss at a position opposite to a bearing portion of a gear housing. The worm wheel contact portion of the bearing portion of the gear housing is provided below the line passing through the center line of the worm shaft and perpendicular to the center line of the worm wheel, and the cover contact portion of the holder is the center portion. It is provided above the line and the maximum outer diameter of each abutting portion is equal to or less than the gear effective diameter of the worm wheel.

According to a second aspect of the present invention, there is provided a motor device with a worm gear, wherein a cushion, which is an elastic member, is provided in a rotation transmission path from the worm wheel to the boss, and the cushion and the cover are in the same phase as the cushion. A rotating elastically deformable plate is provided.

In the motor device with a worm gear according to a third aspect of the present invention, the worm wheel abutting portion of the bearing portion of the gear housing substantially coincides with a line passing through the center line of the worm shaft and perpendicular to the center line of the worm wheel. It is composed of.

[0020]

According to the invention of claim 1, when one of the worm wheels is thrust-displaced, the worm wheel abutting portion of the bearing portion of the gear housing passes through the center line of the worm shaft and is perpendicular to the center line of the worm wheel. Displace the outer gear part of the worm wheel in the bearing direction of the gear housing with a point closest to the worm shaft on a circle with the maximum outer diameter of the abutment portion that is provided in the downward direction and is equal to or less than the effective gear diameter of the worm wheel. As a result, the gear meshing area is increased, and when the worm wheel is thrust in the opposite direction, the holder cover contact portion is provided above the center line and the maximum outer diameter of the contact portion is equal to the worm wheel. The outer peripheral gear part of the worm wheel is geared with the point closest to the worm shaft on the circumference of the wheel effective diameter or less as the fulcrum. The bearing direction of Ujingu is displaced in the opposite direction, it results gear meshing area is increased as the improvement in durability can be obtained.

According to the second aspect of the present invention, at the time of thrust displacement of one of the worm wheels, the worm wheel abutting portion of the bearing portion of the gear housing passes through the center line of the worm shaft and is perpendicular to the center line of the worm wheel. Displace the outer gear part of the worm wheel in the bearing direction of the gear housing with a point closest to the worm shaft on a circle with the maximum outer diameter of the abutment portion that is provided in the downward direction and is equal to or less than the effective gear diameter of the worm wheel. As a result, the gear meshing area is increased, and when the worm wheel thrusts in the opposite direction, contact with the cover via an elastically deformable plate that rotates in the same phase as the cushion on the cushion that is simultaneously displaced. Prevents worm wheel thrust displacement and minimizes the reduction of meshing area For example, improvement of durability can be obtained.

According to the invention of claim 3, the worm wheel abutting portion of the bearing portion of the gear housing is configured to substantially coincide with a line which passes through the center line of the worm shaft and is orthogonal to the center line of the worm wheel. The fulcrum of rotation of the worm wheel during thrust displacement is substantially on the center line in both directions, and as a result, the meshing area is increased in both directions and durability is improved.

[0023]

EXAMPLES Example 1. An embodiment of the invention of claim 1 will be described with reference to FIG. FIG. 1 is an internal structure diagram, and the same or corresponding parts as those of the above-described conventional device are designated by the same reference numerals and the description thereof will be omitted. In the figure, reference numeral 20 denotes a holder, which is placed on the upper end of the outer circumference of the worm wheel 12 and is arranged so as to prevent relative displacement in the axial direction by the snap ring 17 of the boss 7. The holder 20 is arranged in parallel with the cover 18 with a minute clearance, and the maximum outer diameter of the portion having the minute clearance is equal to or smaller than the gear effective diameter of the worm wheel 12.

Next, the operation will be described. At the time of thrust displacement of the worm wheel 12 in the gear housing bearing direction that occurs when the window stops at the lower limit stopper, the worm wheel contact portion 10b of the bearing portion of the gear housing 10 passes through the center line of the worm shaft 9 and the worm wheel 1
A point which is provided below the line perpendicular to the center line of 2 (dimension L) and has a maximum outer diameter of the contact portion 10b which is the closest to the worm shaft 9 on the circumference of the gear effective diameter of the worm wheel 12 or less (N The rotational movement is performed around the (size) as a fulcrum, and as a result, the gear meshing area is increased. In addition, when the worm wheel 12 thrust-displaces in the direction opposite to the gear housing bearing that occurs when the window stops at the upper limit stopper, the cover abutting portion 20a of the holder 20 moves above the center line (H
Dimension) and the maximum outer diameter of the abutting portion 20a is equal to or smaller than the effective gear diameter of the worm wheel 12 on the circumference (a dimension P) closest to the worm shaft 9 as a fulcrum. The gear housing 10 is displaced in the direction opposite to the bearing direction, resulting in an increase in gear meshing area.

FIG. 2 shows a model of the change in the meshing area at this time. In this figure, it is 12d that the worm wheel 12 is constantly rotated around the point G in the direction in which the thrust load is applied, and 1 is the constant rotation of the worm wheel 12 around the point F in the direction in which the thrust load is applied.
2e. As is clear from FIG. 2, the gear meshing area is larger than in the steady state even in each mode, and the durability is improved. The degree of increase in the meshing area at this time increases as the offset distance increases, and increases as the fulcrum distance decreases.

Example 2. An embodiment of the invention of claim 2 will be described with reference to FIG. FIG. 3 is an internal structure diagram, and the same or corresponding parts as those of the above-mentioned conventional one are designated by the same reference numerals and the description thereof will be omitted. In the figure, reference numeral 21 denotes a plate, which is arranged on the upper portion of the cushion 15 and is held by the ring 17 of the boss 7. Further, the plate 21 is arranged in parallel with the cover 18 with a slight clearance.

Next, the operation will be described. At the time of thrust displacement of the worm wheel 12 in the gear housing bearing direction that occurs when the window stops at the lower limit stopper, the worm wheel contact portion 10b of the bearing portion of the gear housing 10 passes through the center line of the worm shaft 9 and the worm wheel 1
A point which is provided below the line perpendicular to the center line of 2 (dimension L) and has a maximum outer diameter of the contact portion 10b which is the closest to the worm shaft 9 on the circumference of the gear effective diameter of the worm wheel 12 or less (N The rotational movement is performed around the (size) as a fulcrum, and as a result, the gear meshing area is increased. Further, at the time of thrust displacement in the direction opposite to the gear housing bearing of the worm wheel 12 that occurs when the window stops at the upper limit stopper, the cushion 15 contacts the cover 18 via the plate 21 to limit the displacement.

The cushion 15 is constructed so that the plate A14 and the plate B13 which are vulcanized and bonded rotate in the same manner as the worm wheel 12 and the boss 7, respectively, and absorb the impact force by bending relative rotation. ing. Further, since the plate 21 elastically changes along the surface of the cushion 15, the deformation of the cushion 15 is not restricted and the impact absorbing ability is not deteriorated. Further, since the cushion 15 and the plate 21 rotate in the same phase,
The durability performance is not deteriorated due to abrasion of the surface of the cushion 15. Also, the plate 2 has the above structure.
The contact noise between the cover 1 and the cover 18 can be suppressed low.

Example 3. An embodiment of the invention of claim 3 will be described with reference to FIG. FIG. 4 is an internal structure diagram, and the same or corresponding parts as those of the above-described conventional one are designated by the same reference numerals and the description thereof will be omitted. In this embodiment, the worm wheel contact portion 10b of the bearing portion of the gear housing 10 is configured to pass through the center line of the worm shaft 9 and substantially coincide with the line perpendicular to the center line of the worm wheel 12.

Next, the operation will be described. At the time of thrust displacement in the gear housing bearing direction of the worm wheel 12 that occurs when the window stops at the lower limit stopper, the worm wheel contact portion 10b of the bearing portion of the gear housing 10 is provided on the center line of the worm shaft 9 and the contact portion. 1
On the circumference of which the maximum outer diameter of 0b is equal to or smaller than the effective gear diameter of the worm wheel 12, a rotational movement is performed with a point (N dimension) closest to the worm shaft 9 as a fulcrum, and as a result, the gear meshing area is increased. Further, even when the worm wheel 12 is thrust-displaced in the opposite direction to the gear housing bearing that occurs when the window stops at the upper limit stopper, the worm shaft has a maximum outer diameter of the abutment portion 10b that is equal to or less than the effective gear diameter of the worm wheel 12. Rotation is performed with a point (Q dimension) farthest from 9 as a fulcrum, and as a result, an increase in gear meshing area can be obtained. However, the amount of each increase is a small amount because the rotation angle is small, but it surely increases.

FIG. 5 shows a model of the change in the meshing area at this time. In this figure, it is 12d that the worm wheel 12 is constantly rotated around the point G in the direction in which the thrust load is applied, and 1 is the constant rotation of the worm wheel 12 around the point F in the direction in which the thrust load is applied.
2e. As is clear from this figure, the gear meshing area in each mode is larger than in the steady state, and the durability is improved. The degree of increase in the meshing area at this time increases as the fulcrum distance decreases.

In each of the first to third embodiments, each of them has been described as a single structure, but by combining the three members with each other, the durability performance can be further improved.

[0033]

As described above, according to the invention of claim 1, the worm wheel and the boss are arranged at the position opposite to the gear housing bearing portion so as to prevent the relative displacement in the axial direction, and the gear housing is provided. The worm wheel abutting portion of the bearing portion of the holder is provided below the line passing through the center line of the worm shaft and perpendicular to the center line of the worm wheel, and the cover abutting portion of the holder is provided above the center line, and By setting the maximum outer diameter of each contact portion to be equal to or less than the gear effective diameter of the worm wheel, the thrust displacement of the worm wheel at the time of impact application can be suppressed even in both directions displacement, and the meshing area of the gear increases and the cushion It is possible to obtain the effect that the durability of can be improved.

According to the second aspect of the invention, a cushion which is an elastic member provided in the rotation transmission path from the worm wheel to the boss, and an elastic deformation which rotates between the cushion and the cover in the same phase as the cushion. By providing a possible plate, it is possible to prevent the thrust displacement of the worm wheel while maintaining the durability of the cushion itself when a shock is applied, so the durability of the cushion can be improved and the contact noise can be suppressed low. The effect of being able to be obtained is obtained.

Further, according to the invention of claim 3, the worm wheel contact portion of the bearing portion of the gear housing is configured to substantially coincide with a line passing through the center line of the worm shaft and perpendicular to the center line of the worm wheel. As a result, the fulcrum of rotation of the worm wheel during thrust displacement is substantially on the center line in both directions, so that the meshing area can be increased even during displacement in both directions.

[Brief description of drawings]

FIG. 1 is an internal structure diagram showing a motor device with a worm gear according to an embodiment of the present invention.

FIG. 2 is a model diagram of a change in gear meshing according to the embodiment of FIG.

FIG. 3 is an internal structure diagram showing a motor device with a worm gear according to an embodiment of the invention of claim 2;

FIG. 4 is an internal structural view showing a motor device with a worm gear according to an embodiment of the invention of claim 3;

FIG. 5 is a model diagram of a change in gear meshing according to the embodiment of FIG.

FIG. 6 is a diagram in which a conventional motor device with a worm gear is mounted on a door of an automobile.

7 is a cross-sectional view taken along the line VII-VII of FIG.

FIG. 8 is a top view of a conventional motor device with a worm gear with a cover removed.

9 is a cross-sectional view taken along the line IX-IX in FIG.

FIG. 10 is an exploded perspective view of FIG.

FIG. 11 is a gear meshing diagram of a conventional worm geared motor device in a steady state.

FIG. 12 is a view as seen from an arrow XII in FIG.

FIG. 13 is a gear meshing diagram of the conventional motor device with a worm gear when the worm shaft clockwise rotation is stopped.

FIG. 14 is a gear meshing diagram of the conventional motor device with a worm gear when the worm shaft counterclockwise rotation is stopped.

[Explanation of symbols]

 7 Boss 8 Motor body 9 Worm shaft 10 Gear housing 12 Worm wheel 15 Cushion 18 Cover 20 Holder 21 Plate

[Procedure amendment]

[Submission date] August 6, 1993

[Procedure Amendment 1]

[Document name to be amended] Statement

[Correction target item name] 0006

[Correction method] Change

[Correction content]

A cushion 15 formed by vulcanizing and adhering the plate A13 and the plate B14 is arranged on the worm wheel 12. Plate A13 convex portion 13a of the outer periphery thereof is inserted into the recess 12c of the worm wheel 12, it is arranged to the same rotation by the convex portions 12 d. The plate B14 has a substantially triangular shape whose inner circumference is a straight line at three points, and is fitted to a substantially triangular portion 7c having a straight line at three points of the tip circle of the boss 7 mounted at the center of the worm wheel 12. Are configured to rotate the same.

[Procedure Amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0012

[Correction method] Change

[Correction content]

The change in meshing depth due to thrust displacement is
As shown in FIGS. 11 to 14, an increase and a decrease occur depending on the rotation direction. FIG. 11 is a diagram showing meshing dimensions in a steady state, and FIG. 12 is a diagram seen from the direction of arrow XII in FIG. FIG. 13 is a diagram showing the displacement when the worm shaft 9 is forcibly stopped during clockwise rotation, and the worm wheel 12 is displaced in the direction opposite to the bearing portion of the worm wheel 12 by the feed angle of the gear. At that time,
As shown in FIG. 9, the worm wheel 12 is offset from the center of the worm shaft 9 by L and rotates about a fulcrum C separated by M, so that its meshing area S ₂
Is smaller than the meshing area S ₁ in the steady state.

[Procedure 3]

[Document name to be amended] Statement

[Correction target item name] 0013

[Correction method] Change

[Correction content]

FIG. 14 is a diagram showing the displacement when the worm shaft 9 is forcibly stopped during counterclockwise rotation. The worm wheel 12 is displaced in the direction of the bearing portion of the worm wheel 12 depending on the feed angle of the gear. To be made. At that time, the worm wheel 12 is warmed as shown in FIG.
Since the shaft 9 is offset from the center of the shaft 9 by L and rotates about a fulcrum G separated by N, its meshing area S ₃ increases compared with the meshing area S ₁ in the steady state.

[Procedure amendment 4]

[Document name to be amended] Statement

[Name of item to be corrected] 0032

[Correction method] Delete

Claims (3)

[Claims] 1. A motor, a gear housing, a worm shaft, which is a motor shaft, and a hole rotatably held in the gear housing, which has a hole into which a boss to be described later can be inserted in a central portion at a right angle to the worm shaft. A worm wheel, a boss that transmits a rotational force to the output shaft, a cushion that is an elastic member provided in a rotation transmission path from the worm wheel to the boss, the worm wheel and the boss, and a bearing of the gear housing. A holder arranged to prevent relative displacement in the axial direction at a position opposite to the gear housing, and a cover that is a lid of the gear housing, wherein a worm wheel contact portion of a bearing portion of the gear housing is the worm shaft. Is provided below the line that passes through the center line of the worm wheel and is perpendicular to the center line of the worm wheel. A worm gear with a motor and wherein the bar abutment portion is provided above the center line, and a gear effective diameter or less of a maximum outer diameter of the worm wheel of the abutment. 2. A motor, a gear housing, a worm shaft, which is a motor shaft, and a hole rotatably held in the gear housing, which has a hole into which a boss to be described later can be inserted in a central portion at a right angle to the worm shaft. A worm wheel, a boss that transmits a rotational force to the output shaft, a cushion that is an elastic member provided in a rotation transmission path from the worm wheel to the boss, a cover that is a lid of the gear housing, and the cushion. A motor device with a worm gear, comprising: an elastically deformable plate that rotates in the same phase as the cushion between a cover and a cover. 3. A motor, a gear housing, a worm shaft, which is a motor shaft, and a hole rotatably held in the gear housing, which has a hole into which a boss to be described later is inserted in a central portion at a right angle to the worm shaft. A worm wheel, a boss that transmits a rotational force to the output shaft, a cushion that is an elastic member provided in a rotation transmission path from the worm wheel to the boss, and a cover that is a lid of the gear housing, A motor device with a worm gear, wherein a worm wheel contact portion of a bearing portion of the housing substantially coincides with a line passing through a center line of the worm shaft and perpendicular to the center line of the worm wheel.