JP2009132167A - Wiper driving device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a wiper driving device capable of rocking a wiper by a one-way turning motor with the usage of a gear transmission mechanism instead of a link mechanism. <P>SOLUTION: In the one-way turning motor 3, a wiper arm 1 is rocked around an axis O<SB>1</SB>through a reduction gear with intersecting axes 20 and the gear transmission mechanism 30, and the gear transmission mechanism 30 is provided with an input shaft 31 and an output shaft 32 on the axis O<SB>1</SB>, and a differential gear mechanism 33 connecting the shafts 31 and 32. The differential gear mechanism 33 is provided with a carrier 34 rotated with the input shaft 31, and is provided with planetary gears 35 and 36 attached to be integrally rotated mutually in an eccentric portion of the carrier 34 offset to a radial direction from the input shaft 31, and is further provided with a fixed gear 37 meshed with the gear 35 and coaxially arranged with the input shaft 31, and an output gear 38 meshed with the gear 36 and fixed to the output shaft 32. A pair of the fixed gear side gears 35 and 37 is the pair of the non-circular gears, and a radius vector of the pitch curve is set so that the output shaft 32 is rocked in spite of one-way turning of the input shaft 31. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a wiper drive device for driving a windshield wiper of a vehicle such as an automobile, and more particularly to an improvement proposal of a wiper drive device that swings a wiper arm via a gear transmission mechanism by a one-way rotation motor.

  A wiper driving device that swings a wiper arm by a one-way rotating motor generally uses a four-bar linkage mechanism that converts one-way rotation from the motor into a swinging motion, and the wiper arm is wiped by this link mechanism. It is common to reciprocate in the interior.

  However, when using the four-bar linkage mechanism that converts the one-way motor rotational movement into the wiper arm swinging movement, the problem of space is that first, a large space is required to store the four-bar linkage mechanism. Arise.

  In addition, since the change in angular velocity and load fluctuation increase when the wiper arm swings from one direction to another in the reverse direction, the four-bar linkage mechanism must be strong enough to withstand it. In addition to being disadvantageous in terms of weight, there is a problem that the wiper blade is likely to have a reduced service life due to a large change in angular velocity and load fluctuation when the wiper arm swings and reversal, and the wiper blade tends to generate wiping noise. is there.

Therefore, conventionally, as described in Patent Document 1, for example, a motor and a wiper arm are drive-coupled between a motor and a wiper arm by a driving device including a cross shaft reduction gear such as a worm gear and a pair of non-circular gears. Increases the storage space efficiency of the drive unit that drives and connects the two, improves the on-board performance of the wiper drive unit, and reduces the change in angular velocity and load fluctuation when the wiper arm swings and reverses, reducing the life of the wiper blade Techniques for suppressing wiping noises have been proposed.
Japanese Patent Laid-Open No. 61-021848

  However, since the conventional wiper driving device switches the rotation direction of the motor to cause the swinging reversal of the wiper arm, the wiper arm needs to reach the boundary position of the wiping area and perform the rocking reversal. Each time it occurs, it is necessary to repeat forward / reverse switching of the motor from the normal rotation state to the reverse rotation state, or from the reverse rotation state to the normal rotation state.

  For this reason, the above-described conventional wiper driving device requires a motor with a large output, requires a large motor with a large capacity, and cannot improve the above-described in-vehicle performance. Cause disadvantages.

In addition, when the motor repeats forward / reverse switching when the wiper arm swings and reverses, not only the above problems and disadvantages related to the motor itself occur,
Excessive load fluctuations occur every time the motor rotation is switched, including the transmission unit that transmits forward / reverse motor rotation to the wiper arm, wiper arm, and wiper blade, and these transmission unit, wiper arm, wiper blade, In addition, problems such as early deterioration of other components and generation of abnormal noises also occur.

  Furthermore, if the motor repeats forward / reverse switching when the wiper arm swings and reverses, the motor rotation speed is always zero once at the time of switching, so there is a limit to increasing the wiper arm swing speed. The concern that the wiping speed of the wiper blade cannot be increased as intended cannot be eliminated.

  In view of such a situation, the present invention is based on a wiper drive device of a type in which a wiper arm swinging and reversing is switched by forward / reverse switching of the motor, and the wiper arm is reciprocally swung by a one-way rotating motor. An object of the present invention is to propose a wiper drive device that does not cause the above-described problems of the wiper drive device described in Patent Document 1.

However, the present invention does not use the above-described general four-bar linkage mechanism that converts the one-way rotation from the motor into a swinging motion, instead of using the latter one-way rotation motor. By using a gear transmission mechanism with a unique configuration that is superior in storage space efficiency and can reduce angular speed change and load fluctuation when the wiper arm swings and reverses,
It is an object of the present invention to propose a wiper driving device which does not cause the above-described problems when a general four-bar linkage mechanism is used.

For this purpose, the wiper drive device according to the invention is as claimed in claim 1,
A wiper driving device that swings a wiper arm via a gear transmission mechanism by a unidirectional rotating motor is a basic premise of the gist configuration, and the gear transmission mechanism is particularly configured as follows to meet the above-mentioned purpose.

In other words, this gear transmission mechanism has an input shaft that receives a one-way rotation from the motor and an output shaft to which the wiper arm is attached facing each other, and is capable of rotational transmission between the input and output shafts. Provided with a differential gear mechanism for drive coupling,
A carrier rotating with the input shaft, and a pair of planets attached to rotate integrally with each other around an axis parallel to the input shaft at an eccentric portion of the carrier that is radially offset from the input shaft. A compound planetary gear set comprising gears, a fixed gear meshed with one of these planetary gears and coaxially arranged on the input shaft, and an output gear meshed with the other planetary gear and secured coaxially to the output shaft.
Then, at least one of the fixed gear side gear pair composed of the one planetary gear and the fixed gear and the output gear side gear pair composed of the other planetary gear and the output gear is a non-circular gear pair, and the pitch in the non-circular gear pair The radius of the curve is set so that the output shaft oscillates despite the one-way rotation of the input shaft.

According to the wiper driving device of the present invention, the one-way rotation of the motor can be converted into a swinging motion by the gear transmission mechanism having the above unique configuration, and this swinging motion is transmitted to the wiper arm to swing it. So that
There is no need to switch the rotation direction of the motor to cause the wiper arm to swing and reverse, and the wiper arm can be swung back and forth with the motor rotating in one direction.
A small motor with a small output is sufficient, and the downsizing of the wiper drive device can improve the in-vehicle performance and is very advantageous in terms of cost.

In addition, when the wiper arm is reciprocally swung by switching between forward and reverse rotation of the motor, the transmission unit that transmits the forward / reverse rotation motor rotation to the wiper arm, the wiper arm, and the wiper blade are excessive each time the motor rotation is switched. Load fluctuation occurs, causing problems such as early deterioration of these transmission parts, wiper arms, wiper blades, and other components, or abnormal noise.
According to the wiper driving device capable of reciprocatingly swinging the wiper arm while rotating the motor in one direction as in the present invention, the excessive load fluctuation associated with the motor rotation switching described above does not occur. Problems such as early deterioration of the transmission unit, wiper arm, wiper blade, and other components, and generation of abnormal noise can be avoided.

Furthermore, when the wiper arm is reciprocally swung by switching the motor forward / reversely, the motor rotation speed is always zero once when the motor is switched forward / reversely. Therefore, the wiper arm swing speed (wiper blade wiping speed) Ca n’t be as high as the goal,
According to the wiper driving device capable of reciprocatingly swinging the wiper arm while rotating the motor in one direction as in the present invention, the rotational speed of the wiper arm (wiper blade) The wiping speed can be increased according to the target without being restricted by this.

By the way, a wiper driving device that swings a wiper arm by a one-way rotating motor generally swings the wiper arm back and forth using a four-bar linkage mechanism that converts one-way rotation from the motor into a swinging motion. Is normal,
In the present invention, the unidirectional rotation of the motor is converted into the reciprocating oscillating motion of the wiper arm by using the gear transmission mechanism of the above-described unique configuration instead of the four-bar linkage mechanism. Since the storage space is not as large as that of the node link mechanism, the wiper drive device can be downsized and its onboard performance can be improved.

In addition, when the wiper arm is reciprocally swung using a four-bar linkage mechanism, it is impossible to take measures against an increase in angular velocity change and load fluctuation when the wiper arm swings in reverse due to its structure.
As in the present invention, when the wiper arm is reciprocally swung using the gear transmission mechanism having the unique configuration described above, the reciprocating swing mode of the wiper arm may be changed depending on the design of the gear transmission mechanism having the unique configuration. Therefore, it is possible to realize even a reciprocal swing of the wiper arm that prevents an increase in angular velocity change and load fluctuation when the wiper arm swing is reversed.

As described above, the change in the angular velocity and the change in the load when the wiper arm swings and swings can be reduced, so that according to the wiper driving device of the present invention, the transmission system from the motor to the wiper arm needs to have a very high strength. This is a great advantage in terms of weight.
Further, since the change in the angular velocity and the load during the reversal of the wiper arm can be reduced, according to the wiper driving device of the present invention, the life of the wiper blade can be extended, and the wiper blade can be wiped from the wiper blade. It is possible to suppress the occurrence of the abnormal noise.

Hereinafter, embodiments of the present invention will be described in detail based on examples shown in the drawings.
1 and 2 show an embodiment of a wiper driving device according to the present invention, FIG. 1 is a diagram showing the actual configuration thereof, and FIG. 2 is a schematic diagram schematically showing a wiper driving system.
This wiper drive unit is used individually for the driver side wiper arm and the passenger side wiper arm, but the configuration is the same in both cases, so only the wiper drive unit for one wiper arm is shown in FIGS. showed that.

In FIGS. 1 and 2, reference numeral 1 denotes a wiper arm, and 2 denotes a wiper blade. When the wiper arm 1 reciprocally swings around the axis O ₁ , the wiper blade 2 wipes the windshield and removes dirt. Shall be removed.
3 is a motor as a power source for swinging the wiper arm 1 around the axis O ₁ , and the rotor 3 is moved only in one direction indicated by an arrow in FIG. 2 by magnetic coupling with the stator 4. A one-way rotating motor that is rotated is used.

The one-way rotary motor 3 is configured to swing the wiper arm 1 around the axis O ₁ through the cross-axis speed reducer 20 and the gear transmission mechanism 30 in order, and the gear transmission mechanism 30 particularly has the following configuration. A gear-type differential gear mechanism is used.
The gear transmission mechanism 30 includes an input shaft 31 to which a one-way rotation from the motor 3 is input and an output shaft 32 to which the wiper arm 1 is attached, on the axis O ₁ so as to be coaxially opposed to each other. A differential gear mechanism 33 for drivingly coupling the shafts 31 and 32 so as to allow rotational transmission is provided.

Differential gear mechanism 33 comprises a carrier 34 that rotates together with the input shaft 31, the eccentric portion of the carrier 34 that is offset from the input shaft 31 in the radial direction, integrally rotates with one another on the input shaft 31 parallel to the axis O ₂ around And a compound planetary gear set including a pair of planetary gears 35 and 36 attached in this manner.
1 and 2 show only one set of compound planetary gear sets consisting of a pair of planetary gears 35 and 36 that rotate integrally, but multiple sets (preferably 3 sets) are set as one set, and are equally spaced in the circumferential direction. It is preferable from the viewpoint of torque transmission balance to be provided.

  The differential gear mechanism 33 further includes a fixed gear 37 that is meshed with the planetary gear 35 closer to the input shaft 31 out of the planetary gears 35 and 36 and is coaxially arranged on the input shaft 31, and the other planetary gear close to the output shaft 32. An output gear 38 meshed with the gear 36 and fixed coaxially to the output shaft 32 is provided.

The motor 3 is arranged so that the rotation axis of the motor output shaft 6 coupled to the rotor 5 and projecting outward has an angle of intersection with the axis O ₁ of the input shaft 31 (both axes are perpendicular to each other in FIGS. 1 and 2). ,
A cross shaft speed reducer 20 is provided at the intersection of the motor output shaft 6 and the input shaft 31 so that the motor output rotation is transmitted from the motor output shaft 6 to the input shaft 31.
The cross shaft speed reducer 20 includes a worm 21 coupled to the motor output shaft 6 and a worm wheel 22 coupled to the input shaft 31. The worm 21 and the worm wheel 22 are engaged with each other.

Thus, the cross-axis speed reducer 20 decelerates the rotation of the motor in a fixed direction from the motor output shaft 6 by the worm 21 and the worm wheel 22 and transmits it to the input shaft 31 to rotate the input shaft 31 in a corresponding fixed direction. At this time, the output axis direction of the motor rotation is bent by the intersection angle (90 degrees) of the motor output shaft 6 and the input shaft 31.
When the motor 3 is arranged such that the rotation axis of the motor output shaft 6 is perpendicular to the axis O ₁ of the input shaft 31, the motor 3 and the motor output shaft 6 are not arranged in tandem with the gear transmission mechanism 30, but are arranged side by side. As a result, the axial dimension of the wiper driving device can be reduced, which contributes to reducing the installation space of the wiper driving device.

With the above configuration, the motor rotation in a certain direction that has reached the input shaft 31 from the motor output shaft 6 via the cross shaft reducer 20 (in FIG. 2, the rotation angle of the input shaft 31 is indicated by θ ₁ ) through which the pivoting about the output axis O ₁ is transmitted to the integral coupling axis compound planetary gear set (planetary gears 35, 36) with.
As a result, the planetary gear 35 rolls around the fixed gear 37, and the rotation of the planetary gear 35 (the rotation angle is indicated by θ ₂ in FIG. 2) is transmitted to the planetary gear 36 as it is. The rotation of the gear 36 (the rotation angle is indicated by θ ₂ in FIG. 2) is transmitted to the output shaft 32 via the output gear 38 (the rotation angle is indicated by θ ₃ in FIG. 2).

In order to make the output shaft 32 (wiper arm 1) swing back and forth while the input shaft 31 is rotated in one direction during transmission of the motor rotation,
At least one of a fixed gear side gear pair composed of the planetary gear 35 and the fixed gear 37 closer to the input shaft 31 and an output gear side gear pair composed of the planetary gear 36 and the output gear 38 close to the output shaft 32 is used as a non-circular gear pair. age,
The radius of the pitch curve in the non-circular gear pair will be described in detail below, but is set so that the output shaft 32 is reciprocally oscillated despite the one-way rotation of the input shaft 31.

First, the conditions for allowing the output shaft 32 (wiper arm 1) to swing back and forth despite the input shaft 31 being rotated in one direction will be described.
As shown in FIG. 2, the radial pitch curve relating to the fixed gear 37 and r _1, the radius of the pitch curve associated with the planetary gear 35 and r _2, the radial pitch curve relating to the output gear 38 r ₃ And the radius of the pitch curve related to the planetary gear 36 is r ₄ and the distance between the axes of the axes O ₁ and O ₂ is a.
The ratio (dθ ₁ / dθ ₃ ) of the rotational angular velocity dθ ₃ of the output shaft 32 to the rotational angular velocity dθ ₁ of the input shaft 31 is
(Dθ ₁ / dθ ₃ ) = 1− (r ₁ · r ₃ ) / (r ₂ · r ₄ ) (1)
However, r ₁ + r ₂ = r ₃ + r ₄ = a (2)
It is represented by

At least one of a fixed gear side gear pair composed of the planetary gear 35 and the fixed gear 37 closer to the input shaft 31 and an output gear side gear pair composed of the planetary gear 36 and the output gear 38 close to the output shaft 32 is used as a non-circular gear pair. In order for the output shaft 32 (wiper arm 1) to swing back and forth despite the one-way rotation of the input shaft 31,
The radius of the pitch curve in the non-circular gear pair needs to be determined for each rotation region during one rotation of the input shaft 31 so that the above equation (1) meets the following conditions.
(Dθ ₁ / dθ ₃ ) = {1- (r ₁ · r ₃ ) / (r ₂ · r ₄ )}> 0 (3)
(Rotation region of the input shaft 31 where the output shaft 32 should be rotated in the same direction as the input shaft 31)
(Dθ ₁ / dθ ₃ ) = {1- (r ₁ · r ₃ ) / (r ₂ · r ₄ )} = 0 (4)
(Rotation region of the input shaft 31 where the output shaft 32 should be stopped regardless of the rotation of the input shaft 31)
(Dθ ₁ / dθ ₃ ) = {1- (r ₁ · r ₃ ) / (r ₂ · r ₄ )} <0 (5)
(Rotation region of the input shaft 31 where the output shaft 32 should be rotated in the opposite direction to the input shaft 31)

That is, in the rotation region of the input shaft 31 where the wiper arm 1 should be swung from the lower reversal position of the swing angle 0 to the upper reversal position of the maximum swing angle, the radius of the pitch curve in the non-circular gear pair is, for example, (3) Determine that the inequality of the equation is satisfied,
In the rotation region of the input shaft 31 where the wiper arm 1 should be swung from the upper reverse position to the lower reverse position, the radius of the pitch curve in the non-circular gear pair, for example, the inequality (5) above is satisfied. Decided to
In the rotation region of the input shaft 31 where the swing direction of the wiper arm 1 is to be reversed at the lower reverse position or the upper reverse position, the radius of the pitch curve in the non-circular gear pair is determined so that the above equation (4) is satisfied. There is a need to.

The output gear side gear pair composed of the planetary gear 36 and the output gear 38 closer to the output shaft 32 is a circular gear pair, and the fixed gear side gear pair composed of the planetary gear 35 and the fixed gear 37 closer to the input shaft 31 is not used. A pair of circular gears,
The displacement curve showing the relationship of the rotation angle θ ₃ of the output shaft 32 to the rotation angle θ ₁ of the input shaft 31 becomes a sine wave curve with one rotation of the input shaft (2π) as one cycle as shown by A1 in FIG. By setting the radius of the pitch curve in the non-circular gear pair (fixed gear side gear pair), the output shaft 32 (wiper arm 1) reciprocally swings between the lower reverse position and the upper reverse position. In this case, the radius of the pitch curve in the non-circular gear pair (fixed gear side gear pair) will be described in detail below.

For the smooth swing required for the wiper arm 1, the displacement curve A1 in FIG. 3 needs to be a smooth curve, and for that purpose, it is a tangential gradient on the displacement curve A1 (dθ ₃ / dθ ₁ ) and the rate of change of the tangential gradient (d ² θ ₃ / dθ ₁ ² ) need to set the radius of the pitch curve in the non-circular gear pair (fixed gear side gear pair). is there.

Hereinafter, it will be described that (dθ ₃ / dθ ₁ ) and (d ² θ ₃ / dθ ₁ ² ) need to change continuously for the smooth swing required for the wiper arm 1. .
When the gear ratio of the output gear side gear pair consisting of the planetary gear 36 and the output gear 38, which is a circular gear pair, is n, the above equation (1) is expressed by the following equation.
(Dθ ₁ / dθ ₃ ) = 1−n (r ₁ / r ₂ ) (6)
By combining this with the above equation (2), the radius radii r ₁ and r ₂ of the pitch curve in the non-circular gear pair (fixed gear side gear pair) can be obtained by the following equations, respectively.
r ₁ = {[1- (dθ ₃ / dθ ₁ )] / [1 + n- (dθ ₃ / dθ ₁ )]} · a (7)
r ₂ = {n / [1 + n− (dθ ₃ / dθ ₁ )]} · a (8)

Further, for smooth swinging required for the wiper arm 1, the planetary gear 35 and the fixed gear 37 that form a non-circular gear pair need to mesh smoothly, and for that purpose, the non-circular gear pair (fixed gear) The radial radius r ₁ and r ₂ of the pitch curve in the side gear pair) must be smoothly changed with respect to the input shaft rotation angle θ ₁ ,
The ratios of the change ratios of the radial radii r ₁ and r ₂ (first-order differential values dr ₁ and dr ₂ ) to the change ratio (first-order differential value dθ ₁ ) of the input shaft rotation angle θ ₁ represented by It needs to change continuously.
(Dr ₁ / dθ ₁ ) = {[− n (d ² θ ₃ / dθ ₁ ² )] / [1 + n− (dθ ₃ / dθ ₁ )] ² } · a (9)
(Dr ₂ / dθ ₁ ) = {[n (d ² θ ₃ / dθ ₁ ² )] / [1 + n− (dθ ₃ / dθ ₁ )] ² } · a (10)

The change ratios (first-order differential values dr ₁ , r ₁ ) of the radial radii r ₁ and r ₂ with respect to the change ratio (first-order differential value dθ ₁ ) of the input shaft rotation angle θ ₁ represented by these equations (9) and (10). In order to continuously change the ratio of dr ₂ ), the tangential gradient on the displacement curve A1 (dθ ₃ / dθ ₁ ) and the rate of change of the tangential gradient (d ² θ ₃ / dθ ₁ ² ) Must change continuously,
It has been proved that (dθ ₃ / dθ ₁ ) and (d ² θ ₃ / dθ ₁ ² ) need to change continuously for the smooth swing required for the wiper arm 1.

Then, by setting the radius radii r ₁ and r ₂ of the pitch curve in the non-circular gear pair (the gear pair of the fixed gear 37 and the planetary gear 35) so as to satisfy this condition, the output with respect to the rotation angle θ ₁ of the input shaft 31 is set. The displacement curve indicating the relationship of the rotation angle θ ₃ of the shaft 32 (wiper arm 1) becomes a smooth curve as indicated by A1 in FIG. 3, and the wiper arm 1 can be smoothly reciprocated as required.

Incidentally, the displacement curve showing the relationship of the rotation angle θ ₃ of the output shaft 32 to the rotation angle θ ₁ of the input shaft 31 is a sinusoidal curve with one rotation of the input shaft (2π) as one cycle as shown by A1 in FIG. When the radial radius r ₁ and r ₂ of the pitch curve in the non-circular gear pair (fixed gear side gear pair) is set,
When the maximum swing angle of the output shaft 32 (wiper arm 1) is δ ₀ as shown in FIG. 3, the rotation angle θ ₃ of the output shaft 32 (wiper arm 1) is the following with respect to the input shaft rotation angle θ ₁ It has an expression relationship.
_{θ 3 = (δ 0/2} ) (1-cosθ 1) ··· (11)

  By substituting the above equation (11) into the above equations (7) and (8), the pitch curves of the planetary gear 35 and the fixed gear 37 forming the non-circular gear pair (fixed gear side gear pair) are shown in FIG. As shown in the figure, the pitch curve can be as smooth as required, and the wiper arm 1 can be swung back and forth smoothly as required.

According to the above-described embodiment, the one-way rotation of the motor 3 is converted into a swinging motion by the gear transmission mechanism 30 having the unique configuration described above with reference to FIGS. 1 and 2, and this swinging motion is transmitted to the wiper arm 1. Because it was made to swing,
It is not necessary to switch the rotation direction of the motor 3 to cause the swing reversal of the wiper arm 1, and the wiper arm 1 can be swung back and forth while rotating the motor 3 in one direction.
The motor 3 can be a small motor with a small output, and the downsizing of the wiper driving device can improve the in-vehicle performance and is very advantageous in terms of cost.

In this embodiment, the motor 3 is arranged such that the rotation axis of the motor output shaft 6 has an angle of intersection with the axis of the input shaft 31, and a cross-axis speed reducer 20 provided at the intersection of the motor output shaft 6 and the input shaft 31. Because rotation is transmitted from the motor output shaft 6 to the input shaft 31 via
The motor 3 is arranged side by side with respect to the gear transmission mechanism 30 and the axial dimension of the wiper drive device can be shortened. This contributes to further downsizing of the wiper drive device and further improves its in-vehicle performance. be able to.

In addition, when the wiper arm is reciprocally swung by switching the forward / reverse rotation of the motor as in the past, the motor rotation switching is also applied to the wiper arm and wiper blade, including the transmission unit that transmits the forward / reverse rotation of the motor to the wiper arm. Excessive load fluctuations occur every time, causing problems such as early deterioration of these transmission parts, wiper arms, wiper blades and other components, or abnormal noise,
According to the wiper driving device that reciprocally swings the wiper arm 1 while rotating the motor 3 in one direction as in the present embodiment, the above load does not occur without excessive load fluctuation caused by the motor rotation switching described above. It is possible to avoid problems such as early deterioration of transmission parts, wiper arms, wiper blades, and other components due to fluctuations, and abnormal noise.

Further, when the wiper arm is reciprocally swung by switching the motor in the forward / reverse direction as in the prior art, the motor rotation speed is always zero when the motor is switched in the forward / reverse rotation. ) Can not be increased as intended,
According to the wiper driving device that reciprocally swings the wiper arm 1 while rotating the motor 3 in one direction as in the present embodiment, the motor rotation speed never becomes zero, and the wiper arm 1 swing speed The (wiping speed of the wiper blade) can be increased as intended without being restricted by this.

In general, when the wiper arm is swung by a one-way rotating motor, it is common to use a four-bar linkage mechanism that converts the one-way rotation from the motor into a swinging motion as described above. There are
In this embodiment, instead of the above four-link mechanism, the one-way rotation of the motor 3 is converted into the reciprocating swinging motion of the wiper arm 1 using the gear transmission mechanism 30 having the unique configuration described above with reference to FIGS. Therefore, since the gear transmission mechanism 30 does not require a storage space as large as the four-bar linkage mechanism, the wiper drive device can be downsized and its onboard performance can be improved.

In addition, when the wiper arm is reciprocally swung using the above-described general four-bar linkage mechanism, it is impossible to take measures against an increase in angular velocity change or load fluctuation when the wiper arm swings in reverse due to its structure.
When the wiper arm 1 is reciprocally swung using the gear transmission mechanism 30 having the unique configuration described above with reference to FIGS. 1 and 2 as in this embodiment, the design of the gear transmission mechanism 30 having the unique configuration (radial radius r) is used. ₁ and r ₂ ) Depending on how the reciprocating swing mode of the wiper arm 1 can be set in any way,
It is possible to realize reciprocal swinging of the wiper arm that prevents an increase in change in angular velocity and load when the wiper arm 1 swings and reverses.

As described above, the change in the angular velocity and the change in the load during the reversal of the swing of the wiper arm 1 can be reduced, so that according to the wiper driving device of the present embodiment, the transmission system from the motor 3 to the wiper arm 1 has a great strength. There is no need to have a large weight, which is very advantageous in terms of weight.
In addition, since the change in the angular velocity and the load when the wiper arm 1 swings can be reduced, according to the wiper driving device of the present embodiment, the life of the wiper blade 2 can be extended, and the wiper blade Generation of noise from wiping off 2 can be suppressed.

Further, in this embodiment, the output gear side gear pair 36, 38 is a circular gear pair, the fixed gear side gear pair 35, 37 is a non-circular gear pair,
Displacement curve A1 indicating the rotation angle theta ₃ of relationship between the output shaft 32 with respect to the rotation angle theta ₁ of the input shaft 31 as shown in FIG. 3, continuous change d [theta] ₃ / d [theta] ₁ and d ² θ ₃ / _{dθ 1} ² is In addition, radiuses r ₂ and r ₁ of the pitch curves in the non-circular gear pairs 35 and 37 are set so that the output shaft 32 oscillates between the lower inversion position and the upper inversion position of the displacement curve A1. Because we set
The wiper arm 1 can be smoothly reciprocally swung between the lower reversing position and the upper reversing position, and the uncomfortable feeling that the swing speed of the wiper arm 1 becomes discontinuous in the wiping region can be wiped off.

Further, in this embodiment, as shown in FIG. 3, a displacement curve A1 showing the relationship of the rotation angle θ ₂ of the output shaft 32 to the rotation angle θ ₁ of the input shaft 31 is a sine wave curve with one rotation of the input shaft as one cycle. By setting the radial radius r ₂ , r ₁ of the pitch curve in the non-circular gear pair 35, 37 so that the wiper arm 1 reciprocally swings between the lower inversion position and the upper inversion position of the displacement curve A1 Because
The smooth reciprocating swing of the wiper arm 1 described above can be further ensured, and the uncomfortable feeling that the swing speed of the wiper arm 1 becomes discontinuous in the wiping region can be wiped off more reliably.

In the above description, the case where the fixed gear side gear pair including the planetary gear 35 and the fixed gear 37 is a non-circular gear pair and the output gear side gear pair including the planetary gear 36 and the output gear 38 is a circular gear pair has been described. But,
Conversely, when the output gear side gear pair composed of the planetary gear 36 and the output gear 38 is a non-circular gear pair, and the fixed gear side gear pair composed of the planetary gear 35 and the fixed gear 37 is a circular gear pair,
When both the fixed gear side gear pair and the output gear side gear pair are non-circular gear pairs, the same effect can be obtained by setting the radius of the pitch curve in the non-circular gear pair based on the same concept. Needless to say.

While following the configuration of FIGS. 1 and ₂ , the radiuses r ₂ and r ₁ of the pitch curve in the fixed gear side gear pair (non-circular gear pair) composed of the planetary gear 35 and the fixed gear 37 are made different from the above. Various displacement curves different from the displacement curve indicated by A1 in FIG. 3 can be realized as follows.
In all the following embodiments, the fixed gear side gear pair composed of the planetary gear 35 and the fixed gear 37 is a non-circular gear pair, and the output gear side gear pair composed of the planetary gear 36 and the output gear 38 is a circular gear pair. The explanation will be expanded sequentially.

The displacement curve A2 in FIG. 5 shows that the former period is shorter than the latter period in the section from the lower inversion position to the upper inversion position α ₀ and in the section from the upper inversion position α ₀ to the lower inversion position. This is a sinusoidal curve with different periods. However, the sinusoidal curve as a whole has one rotation of the input shaft as one period, and is smoothly continuous at the lower inversion position and the upper inversion position. It is a curve.
In this case, the rotation angle θ ₃ of the output shaft 32 (wiper arm 1) has the following relationship with the input shaft rotation angle θ ₁ .
Interval where the input shaft rotation angle θ ₁ is 0 ≦ θ ₁ ≦ α ₀ ≠ π:
_{θ 3 = (δ 0/2} ) {1-cos (π / α 0) θ 1} ··· (12)
Section where input shaft rotation angle θ ₁ is α ₀ <θ ₁ ≦ 2π:
_{θ 3 = (δ 0/2} ) {1 + cos (π / [2π-α 0]) (θ 1 -α 0)} ··· (13)

In the present embodiment, the radial radius r ₂ of the pitch curve in the fixed gear side gear pair (non-circular gear pair) composed of the planetary gear 35 and the fixed gear 37 so that the displacement curve A2 becomes the smooth sine wave curve described above. r ₁ is set.
Here, the upper reversal position α ₀ can be arbitrarily determined, whereby the wiper external payment speed from the lower reverse position to the upper reverse position and the wiper internal payment speed from the reverse upper reverse position to the lower reverse position are determined. There is a practical advantage that can be freely varied depending on the application.

  By substituting the above equations (12) and (13) into the above equations (7) and (8), the planetary gear 35 and the fixed gear 37 forming the non-circular gear pair (fixed gear side gear pair) The pitch curve can be obtained as shown in FIG. 6. As shown in the figure, the pitch curve can be a smooth curve as required, and the wiper arm 1 can be swung back and forth smoothly as required.

Displacement curve A3 in Fig. 7, only small sections gamma _L from the lower reversing position, also a curve rotating stop upper reversing position alpha ₀ from a minute interval gamma _U only the output shaft 32 (the wiper arm 1).
In this case, the rotation angle θ ₃ of the output shaft 32 (wiper arm 1) has the following relationship with the input shaft rotation angle θ ₁ .
Section where input shaft rotation angle θ ₁ is 0 ≦ θ ₁ ≦ γ _L :
θ ₃ = 0 (14)
Section where input shaft rotation angle θ ₁ is γ _L <θ ₁ ≦ α ₀ :
_{θ 3 = (δ 0/2} ) {1-cos (π / [α 0 -γ L]) (θ 1 -γ L)} ··· (15)
Section where input shaft rotation angle θ ₁ is α ₀ <θ ₁ ≦ α ₀ + γ _U :
θ ₃ = δ ₀ (16)
Section where the input shaft rotation angle θ ₁ is α ₀ + γ _U <θ ₁ ≦ 2π:
_{θ 3 = (δ 0/2} ) {1 + cos (π / [2π-α 0 -γ U]) (θ 1 -α 0 -γ U)} ··· (17)

In the present embodiment, the fixed gear side gear pair (non-circular gear pair) composed of the planetary gear 35 and the fixed gear 37 so that the displacement curve A3 is a curve having the rotation stop section of the output shaft 32 (wiper arm 1). ) To set the radius r ₂ and r ₁ of the pitch curve.
By using the displacement curve A3 having the rotation stop section of the output shaft 32 (wiper arm 1), it is possible to avoid a large load fluctuation at the time of reversing at the lower reversing position and the upper reversing position. It is possible to avoid problems such as early deterioration of transmission parts, wiper arms, wiper blades, and other components due to fluctuations, and abnormal noise.

  Non-circular gear pair (fixed gear side gear pair) by substituting the above-mentioned formulas (14), (15), (16) and (17) into the above-mentioned formulas (7) and (8) The pitch curve of the planetary gear 35 and the fixed gear 37 that form the shaft can be obtained as shown in FIG. 8, and the pitch curve can be made smooth as required as shown in the figure, and the wiper arm 1 reciprocates smoothly as required. It can be swung.

  FIG. 9 shows the wiper driving device shown in FIGS. 1 and 2 as shown in FIG. 10 (1d: wiper arm, 2d: wiper blade, 3d: motor, 30d: gear transmission mechanism), and assistant. Displacement curve A4 suitable for the driver side wiper drive device when used individually as the drive device for the seat side wiper (1p: wiper arm, 2p: wiper blade, 3p: motor, 30p: gear transmission mechanism), and The displacement curve A5 suitable for the passenger seat side wiper drive device is shown.

In this embodiment, as the direction of the maximum oscillation angle [delta] _0p passenger side wiper than the maximum swing angle [delta] _0d driver's side wiper increases, displacement curve A4 driver's side wiper driving apparatus, and the passenger The displacement curve A5 of the seat-side wiper drive device is defined as shown in FIG. 9, and the fixed gear side gear pair (non-rotating gear) of the driver-side wiper drive device and the passenger-side wiper drive device is obtained so that these displacement curves A4, A5 are obtained The radial radius r ₂ and r ₁ of the pitch curve in the circular gear pair) 35 and 37 are set.

Such a to be larger than the maximum swing angle [delta] _0d driver side wiper maximum oscillation angle [delta] _0p passenger side wiper, wiping the passenger side wiper blade 2p on the windshield W shown in FIG. 10 As is clear from the comparison between the wiping area and the wiping area of the driver-side wiper blade 2d on the windshield W, the wiping area should be made larger by the hatching area S than when δ _0p = δ _0d. Can do.
And because this wiping area increasing region S is located closer to the driver's seat, and because the driver's seat front region to be wiped off by both the driver's seat side wiper blade 2d and the passenger side wiper blade 2p is enlarged. For these two reasons, the driving field of view is kept good and helps safe driving.

As shown in FIGS. 9 and 10, the wiper driving device shown in FIGS. 1 and 2 is used individually as the driving device for the driver's side wiper and the driving device for the passenger's side wiper, and the maximum swing angle δ _0p of the passenger side wiper is Even when it is larger than the maximum swing angle δ _0d of the driver side wiper,
For both wiper driving devices, the above-mentioned concept is applied to FIG. 7, and the driver seat side displacement curve A4 as shown in FIG. 11 is changed from the lower inversion position to the minute interval γ _{Ld and} from the upper inversion position α _0. Set the section where the output shaft 32 (wiper arm 1d) stops rotating by the minute section γ _Ud , and also on the passenger seat side displacement curve A5 by the minute section γ _Lp from the lower inversion position and slightly from the upper inversion position α ₀ By setting a section in which the rotation of the output shaft 32 (wiper arm 1d) is stopped by the section γ _Up, the same operation and effect can be achieved according to the embodiment of FIG.

However, in this embodiment, as shown in FIG. 11, the rotation stop section γ _Ld and γ _Lp of the output shaft 32 (wiper arms 1d, 1p) in the downward inversion position has a relationship of γ _Ld <γ _Lp , and the inversion is downward In the position, the rotation stop section γ _Lp of the passenger-side wiper arm 1p is made longer than the rotation stop section γ _Ld of the driver-side wiper arm 1d,
The rotation stop section γ _Ud and γ _Up of the output shaft 32 (wiper arms 1d, 1p) at the upper reversing position has a relationship of γ _Ud > γ _Up , and at the upper reversing position, the rotation of the driver side wiper arm 1d is stopped. The rotation stop section γ _Up of the passenger side wiper arm 1p is made shorter than the section γ _Ud .

Thus, the rotation stop section γ _Lp of the passenger side wiper arm 1p is longer than the rotation stop section γ _Ld of the driver's seat side wiper arm 1d in the downward inversion position, and the driver seat side wiper arm 1d The driver seat side displacement curve A4 and the passenger seat side displacement curve A5 in FIG. 11 in which the rotation stop section γ _Up of the passenger seat side wiper arm 1p is shorter than the rotation stop section γ _Ud are described above (14). In Expressions (17) to (17), it is obtained by substituting δ _0d or δ _0p for δ ₀ .
As described above, the driver seat side wiper arm 1d and the passenger seat side wiper are provided with the relationship of γ _Ld <γ _{Lp at} the lower inversion position and the relationship of γ _Ud > γ _{Up at} the upper inversion position. It is possible to prevent the arms 1p from interfering with each other while swinging.

In each of the above-described embodiments, the wiper driving device of FIGS. 1 and 2 is individually used as the driving device for the driver's seat side wiper and the driving device for the front passenger side wiper.
According to the configuration illustrated in FIGS. 12 and 13, the driver's seat side wiper and the passenger's seat side wiper can be driven by one common one-way rotation motor 3.

  The unidirectional rotating motor 3 used in this embodiment of FIGS. 12 and 13 is basically the same as the motor 3 in FIGS. 1 and 2, but rotates together with the rotor 5 driven by magnetic coupling with the stator 4. A motor output shaft 6d for the driver's seat side wiper and a motor output shaft 6p for the passenger's seat side wiper are provided as motor output shafts, and these are fixed coaxially to the rotor 5 and protrude from both ends of the motor 3.

The motor output shaft 6d swings the driver's seat side wiper arm 1d (see FIG. 13) around the axis O _1d through the cross shaft speed reducer 20d and the gear transmission mechanism 30d sequentially.
Motor output shaft 6p shall swinging sequentially through the cross-axis reduction gear 20p and gear transmission mechanism 30p passenger side wiper arm 1p (see Fig. 13) around the axis O _1p.

The cross-axis speed reducer 20d and the gear transmission mechanism 30d for the driver-side wiper and the cross-axis speed reducer 20p and the gear transmission mechanism 30p for the passenger-side wiper are respectively the cross-axis speed reduction described above with reference to FIGS. The same configuration as the machine 20 and the gear transmission mechanism 30
Accordingly, to the same components as those in the cross shaft reduction gear 20 and the gear transmission mechanism 30, the suffix “d” for the driver seat and the suffix “p” for the passenger seat are added to the same reference numerals. The illustration was given with reference numerals, and duplicated explanations were avoided.
It should be noted that not only the symbols attached to the component parts but also symbols such as the axes O ₁ and O ₂ and the rotation angles θ ₁ , θ ₂ , and θ ₃ are attached to the same symbol on the driver's seat side with the suffix “d ", And the one on the passenger seat side is indicated by the same symbol with the suffix" p ".

When mounting the above wiper drive device on a vehicle, as shown in FIG.
The driver side wiper arm 1d is connected to the output shaft 32d of the gear transmission mechanism 30d, and the passenger seat side wiper arm 1p is connected to the output shaft 32p of the gear transmission mechanism 30p for practical use.

The output gear side gear pair composed of the planetary gears 36d, 36p and the output gears 38d, 38p is formed as a circular gear pair, and the fixed gear side gear pair composed of the planetary gears 35d, 35p and the fixed gears 37d, 37p is defined as a non-circular gear pair. And none,
By determining the radius of the pitch curve in the fixed gear side gear pair (non-circular gear pair) composed of the latter planetary gears 35d and 35p and the fixed gears 37d and 37p in the same manner as in the above embodiments,
The driver's seat side wiper arm 1d and the passenger's side wiper arm 1p swing back and forth between, for example, a downward inversion position indicated by a solid line in FIG. 14 and an upward inversion position indicated by a broken line, respectively. By wiping off the windshield W, dirt can be removed.

By the way, according to the present embodiment, the driver-side wiper and the passenger-side wiper are configured to be reciprocally swung by one common one-way rotation motor 3,
Using two motors 3 for the driver's side wiper and the passenger's side wiper, the configuration can be made simpler and more compact than the previous embodiment, and the installation space and cost can be reduced. In addition to being advantageous, it is also possible to expect an improvement in fuel consumption due to weight reduction.

In this embodiment, the two motor output shafts of the driver seat side motor output shaft 6d and the passenger seat side motor output shaft 6p are projected from both ends of the motor 3,
The motor output shaft is only one projecting from one end of the motor 3, and the driver's seat side wiper arm 1d is drivingly coupled to the cross shaft reduction gear 20d and the gear transmission mechanism 30d sequentially, and the cross shaft reduction gear 20p. Needless to say, the passenger seat side wiper arm 1p may be driven and coupled through the gear transmission mechanism 30p in sequence.

By the way, when the motor 3 is shared between the driver-side wiper driving device and the passenger-side wiper driving device according to the configuration of FIGS.
The twist direction of the teeth of the worm 21d in the driver's seat side cross-axis reducer 20d and the twist direction of the teeth of the worm 21p in the passenger's side cross-axis reducer 20p are the same direction, and the driver's seat side wiper and the passenger's seat side wiper Are set to the radial radius r ₂ and r ₁ of the pitch curve in the fixed gear side gear pair (non-circular gear pair) composed of the planetary gears 35d and 35p and the fixed gears 37d and 37p, respectively. Is good.
In this case, the gear transmission mechanism 30d on the driver's seat side and the gear transmission mechanism 30p on the passenger seat side can have exactly the same configuration and specifications, which is very advantageous in terms of cost and parts management, The work can be simplified.

FIG. 15 shows still another embodiment of the present invention. In this embodiment, the configuration is basically the same as that of the embodiment in FIGS. The twisting direction of the teeth of the driver side worm 21d and the twisting direction of the teeth of the passenger side worm 21p forming the passenger side cross-axis speed reducer 20p are opposite to each other.
Accordingly, the driver seat side worm wheel 22d and the passenger seat side worm wheel 22p, which mesh with the driver seat side worm 21d and the passenger seat side worm 21p, respectively, have tooth inclination directions opposite to each other.

Further, in this embodiment, the driver's seat side wiper and the passenger's seat side wiper are clearly shown from the driver's seat side displacement curve A4 shown in Fig. 16 (a) and the passenger's seat side displacement curve A5 shown in Fig. 16 (b). The radius radii r ₂ and r ₁ of the pitch curve in the fixed gear side gear pair (non-circular gear pair) composed of the planetary gears 35d and 35p and the fixed gears 37d and 37p are set so as to be oscillated in opposite phases.

Also in this embodiment having such a configuration, the driver-side wiper and the passenger-side wiper are reciprocally swung by a common one-way rotating motor 3, so that the configuration is simple and compact. This is advantageous in terms of installation space and cost, and can greatly reduce the weight.
Since the twisting direction of the teeth of the driver side worm 21d and the twisting direction of the teeth of the passenger side worm 21p are opposite to each other, the thrust acting on the motor output shafts 6d and 6p is also opposite to each other. As a result of the cancellation of the thrust, it is not necessary to consider the thrust when designing and mounting the motor 3, which is advantageous.

FIG. 17 shows still another embodiment of the present invention. In this embodiment, the one-way rotary motor 3 shared by the driver's seat side wiper and the passenger's seat side wiper is replaced with a motor output shaft 6d, Unlike the case where 6p is driven by the common rotor 5, the motor output shafts 6d and 6p are individually driven by the individual rotors 5o and 5i.
That is, the motor 3 in the present embodiment is provided with the inner rotor 5i and the outer rotor 5o coaxially on the inner and outer circumferences of one stator 4, and the inner rotor 5i and the outer rotor 5o are respectively connected to the common stator 4. It is assumed that they are individually rotated by magnetic coupling.

In this embodiment, the motor 3 is a radial gap type composite motor including one stator 4 and inner and outer rotors 5i and 5o on the inner and outer circumferences.
The present invention is not limited to this, and it goes without saying that an axial gap type composite motor may be used in which two rotors are arranged on both sides in the axial direction of one stator and these rotors are individually driven to rotate by magnetic coupling with the stator.

In any case, the driver side wiper is connected to one of the two rotors, and the passenger side wiper is connected to the other.
In FIG. 17, the driver side wiper with the larger wiping load of the driver side wiper and the passenger side wiper is coupled to the outer rotor 5o having a large rotation effective diameter and a large output torque, and the other passenger side The wiper is coupled to the inner rotor 5i having a small effective rotation diameter and a small output torque so that the motor 3 can be a small motor having a small output.

For this reason, the motor output shaft 6d used for driving the driver's seat side wiper is coaxially connected to the outer rotor 5o and protrudes from the corresponding end of the motor 3, and the motor output used for driving the passenger's seat side wiper The shaft 6p is coaxially connected to the inner rotor 5i and protrudes from the corresponding end of the motor 3.
The motor output shaft 6d is coupled to the driver's seat side wiper arm 1d sequentially through the cross shaft reduction gear 20d and the gear transmission mechanism 30d as described above with reference to FIGS. 12 and 13, and the motor output shaft 6p is also illustrated in FIG. , 13 is coupled to the passenger side wiper arm 1p through the cross shaft reduction gear 20p and the gear transmission mechanism 30p in order.

When mounting the wiper driving device on a vehicle, in the same manner as described above with reference to FIG. 14, it is disposed and mounted below the windshield W as shown in FIG.
At this time, the driver's seat side wiper arm 1d and the passenger's side wiper arm 1p are arranged so as to overlap in the wiping direction as the wiper blades 2d, 2p mutually indicate OL in the inoperative position.

Also, so that the maximum oscillation angle [delta] _0p passenger side wiper is larger than the maximum swing angle [delta] _0p of the driver's seat side wiper, planet gears 35d, 35p and the fixing gear 37d, fixed wheel-side gear pair consisting of 37 p ( The radius of the pitch curve in the non-circular gear pair) is determined in the same manner as in the examples in FIGS.
As a result, the driver's seat side wiper arm 1d and the passenger's side wiper arm 1p reciprocally swing, for example, between a lower inversion position indicated by a solid line in FIG. 18 and an upper inversion position indicated by a broken line, respectively. The dirt can be removed by wiping the windshield W with 2d and 2p.

Since the composite motor 3 in this embodiment can individually control the rotation speed of the outer rotor 5o and the inner rotor 5i,
The driver-side wiper blade 2d and the passenger-side wiper blade 2p overlap each other in the wiping direction as indicated by OL, and the maximum swing angle δ _0p of the passenger-side wiper is the maximum swing angle of the driver-side wiper. Even if it is larger than δ _0p , the driver-side wiper blade 2d and the passenger-side wiper blade 2p do not interfere with each other.
Overlap OL of the wiper blade 2d and passenger's side wiper blade 2p, the magnitude relationship between the maximum oscillation angle [delta] _0p maximum oscillation angle [delta] _0p and driver side wiper passenger side wiper, the driver's side The wiper blade wiping area can be enlarged and a good driving field of view can be secured.

When the motor 3 is composed of a composite motor as shown in FIG. 17, the outer rotor 5o and the inner rotor 5i can individually control not only the rotation speed but also the rotation direction.
Therefore, as shown in FIG. 19, which schematically shows the wiper driving device of FIG. 17, the outer rotor 5o and the inner rotor 5i can be rotated in opposite directions.
In this case, the reaction force acting on the stator 4 of the composite motor 3 can be canceled by the outer rotor 5o and the inner rotor 5i, so that it is not necessary to increase the rigidity at the mounting portion of the stator 4, and the motor 3 is configured more compactly. be able to.

Thus, when the outer rotor 5o and the inner rotor 5i are rotated in opposite directions, the driver seat side worm 21d and the passenger seat side worm 21p driven by the outer rotor 5o and the inner rotor 5i are also shown in FIG. A fixed gear side gear pair consisting of planetary gears 35d, 35p and fixed gears 37d, 37p so that the twisting directions of the teeth are opposite to each other and the driver side wiper and the passenger side wiper are swung in the same phase ( The radiuses r ₂ and r ₁ of the pitch curve in the non-circular gear pair) are set.
According to such a configuration, the driver seat side gear transmission mechanism 30d and the passenger seat side gear transmission mechanism 30p of the same specification can swing the driver seat side wiper and the passenger seat side wiper in the same phase, which greatly reduces the cost. It is advantageous.

In the case where the motor 3 is composed of a composite motor as shown in FIG. 17, as shown in FIG. 20 schematically showing the wiper driving device of FIG.
Rotate the outer rotor 5o and the inner rotor 5i in opposite directions (same as in the embodiment of FIG. 19)
As shown in FIG. 20, the twisting directions of the teeth of the driver side worm 21d and the passenger side worm 21p driven by the outer rotor 5o and the inner rotor 5i are opposite to each other, unlike the embodiment of FIG. In addition, the movement of the pitch curve in the fixed gear side gear pair (non-circular gear pair) composed of the planetary gears 35d and 35p and the fixed gears 37d and 37p so that the driver side wiper and the passenger side wiper are swung in opposite phases. The diameters r ₂ and r ₁ may be set respectively.

  According to the present embodiment having such a configuration, by rotating the outer rotor 5o and the inner rotor 5i in opposite directions, the reaction force acting on the stator 4 of the composite motor 3 is applied to the outer rotor as in the embodiment of FIG. The offset between 5o and the inner rotor 5i can be offset, and there is no need to increase the rigidity at the mounting portion of the stator 4, and the motor 3 can be made more compact.

Further, as in this embodiment, the twisting directions of the teeth of the driver seat side worm 21d and the passenger seat worm 21p are opposite to each other, and the driver seat side wiper and the passenger seat side wiper are swung in opposite phases. If configured,
The same effect as the embodiment of FIG. 19, that is, the driver side wiper and the passenger side wiper are swung in the same phase by the driver side gear transmission mechanism 30d and the passenger side gear transmission mechanism 30p of the same specification. Therefore, it is possible to achieve an effect that is very advantageous in terms of cost.

  Even when any of the above-described embodiments is used, when the driver-side wiper driving device and the passenger-side wiper driving device are used in one set in the vehicle, the driving mode of the driver-side wiper and the driving of the passenger-side wiper The combination with the mode can be automatically controlled as follows according to the raindrop amount detection value R from the raindrop detection means (not shown) that detects the raindrop amount that reaches the windshield W.

As will be described in detail with reference to FIG. 21, the raindrop amount detection value R is compared with the first minute raindrop amount setting value R1 and the second large raindrop amount setting value R2, and the raindrop amount detection value R is 0, or the wiper When it is determined that the amount is very small (R <R1) that is not enough to activate the engine, both the driver side wiper and the passenger side wiper are stopped as shown in Fig. 21 (a). In addition, the two rotors 5o and 5i of the composite motor 3 are driven and controlled so that the driver-side wiper swing angle θ _3d and the passenger-side wiper swing angle θ _3p are both kept at zero.

  If it is determined that the raindrop detection value R is greater than or equal to the first minute raindrop amount setting value R1, but less than the second large raindrop amount setting value R2 (R1 ≦ R <R2), the raindrop amount The combination of the driving mode of the driver seat side wiper and the driving mode of the passenger seat side wiper according to the magnitude of the detected value R is as follows.

In other words, if this raindrop detection value R is a semi-dry time that is a small value close to the first minute raindrop amount setting value R1, the driver seat side wiper swing angle θ _3d and the passenger seat side in FIG. 21 (b) As indicated by the frequency of occurrence of the wiper swing angle θ _3p , the passenger-side wiper is operated once for the driver-side wiper being operated multiple times,
If the raindrop amount detection value R is a semi-wet value that is a large value close to the second raindrop amount setting value R2, the driver-side wiper swing angle θ _3d and the passenger-side wiper swing angle in FIG. 21 (c) As shown by the frequency of θ _3p , the composite motor 3 is operated so that the passenger-side wiper is operated multiple times (however, fewer times than the driver-side wiper is operated multiple times) with respect to the multiple operations of the driver-side wiper. The two rotors 5o, 5i are driven and controlled.

Then, as the raindrop amount detection value R increases from a small value near the first minute raindrop amount setting value R1 toward a large value near the second raindrop amount setting value R2, from the operation mode of FIG. Change the wiper operation mode to the operation mode of FIG. (C), and gradually increase the number of operations of the passenger side wiper for multiple operations of the driver side wiper,
The passenger-side wiper is operated at the minimum frequency necessary to ensure the driving view of the windshield.
By doing so, the driving field of view can be ensured with minimum motor power consumption, and the battery life can be extended.

In the wet state, when the raindrop amount detection value R is determined to be a large value that is equal to or greater than the second raindrop amount setting value R2 (R ≧ R2), the driver seat side wiper swing angle θ _{3p in} FIG. As shown by the frequency of occurrence of the passenger-side wiper swing angle θ _3d , the two rotors 5d and 5p of the composite motor 3 are driven and controlled so that both the driver-side wiper and the passenger-side wiper operate without restriction. .

1 is an overall perspective view showing the actual configuration of a wiper drive device according to an embodiment of the present invention. It is a basic diagram which shows typically the wiper drive system of the wiper drive device which becomes the Example. It is a wave form diagram of a displacement curve showing the relation of the output shaft rotation angle to the input shaft rotation angle of the gear transmission mechanism in the wiper drive device of the same embodiment. It is explanatory drawing which shows the pitch curve of the non-circular gear pair which comprises the gear transmission mechanism in the wiper drive device of the Example. FIG. 4 is a waveform diagram similar to FIG. 3, showing a displacement curve of a gear transmission mechanism used in a wiper drive device according to another embodiment of the present invention. FIG. 5 is an explanatory view similar to FIG. 4, showing a pitch curve of a non-circular gear pair constituting a gear transmission mechanism in the wiper drive device of the same embodiment. FIG. 6 is a waveform diagram similar to FIG. 3, showing a displacement curve of a gear transmission mechanism used in a wiper drive device according to still another embodiment of the present invention. FIG. 5 is an explanatory view similar to FIG. 4, showing a pitch curve of a non-circular gear pair constituting a gear transmission mechanism in the wiper drive device of the same embodiment. FIG. 4 is a waveform diagram similar to FIG. 3, showing displacement curves of the driver seat side gear transmission mechanism and the passenger seat side gear transmission mechanism when the driver seat side wiper drive device and the passenger seat side wiper drive device are used as a set. FIG. 10 is an explanatory diagram showing installation points of a driver seat side wiper driving device and a passenger seat side wiper driving device that exhibit the displacement curve of FIG. 9, and wiper wiping areas by these wiper driving devices. FIG. 3 is a waveform diagram similar to FIG. 3, showing a modification of the displacement curve of the driver-side gear transmission mechanism and the passenger-side gear transmission mechanism when the driver-side wiper drive device and the passenger-side wiper drive device are used as a set. It is. FIG. 10 is an overall perspective view showing the actual configuration of a wiper drive device according to yet another embodiment of the present invention configured to drive a driver seat side wiper and a passenger seat side wiper with one motor. It is a basic diagram which shows typically the driver's seat side wiper drive system and front passenger's seat side wiper drive system of the wiper drive device which becomes the same Example. It is explanatory drawing which shows the installation point of the wiper drive device which becomes the Example, and the driver's seat side wiper wiping area | region and front passenger side wiper wiping area | region by this wiper drive device. FIG. 14 is a schematic diagram similar to FIG. 13, schematically showing a driver seat side wiper drive system and a passenger seat side wiper drive system of a wiper drive device according to still another embodiment of the present invention; FIG. 6 is a waveform diagram showing a displacement curve of the wiper drive device according to the embodiment, where (a) is a waveform diagram related to a displacement curve of the driver side gear transmission mechanism, (b) is a displacement curve of the passenger side gear transmission mechanism. FIG. FIG. 10 is an overall perspective view showing the actual configuration of a wiper driving device according to still another embodiment of the present invention configured to drive a driver seat side wiper and a passenger seat side wiper with one motor. It is explanatory drawing which shows the installation point of the wiper drive device which becomes the same Example, and the driver's seat side wiper wiping area | region and front passenger side wiper wiping area | region by this wiper drive device. It is the basic diagram which showed typically the driver's seat side wiper drive system and passenger's seat side wiper drive system of the wiper drive device which becomes the same example, and also illustrated the component of the modification. FIG. 20 is a schematic diagram similar to FIG. 19, schematically showing a driver seat side wiper drive system and a passenger seat side wiper drive system of a wiper drive device according to still another embodiment of the present invention; A time chart showing a combination of a driver-side wiper drive control mode and a passenger-side wiper drive control mode when the driver-side wiper drive device and the passenger-side wiper drive device are used as a set, (a) (B) is a time chart for semi-dry, (c) is a time chart for semi-wet, and (d) is a time chart for wet.

Explanation of symbols

1 Wiper arm
1d Wiper arm on driver's side
1p Wiper arm on the passenger side 2 Wiper blade
2d Wiper blade on driver's side
2p Passenger side wiper blade 3 One-way rotating motor 4 Stator 5 Rotor
5i inner rotor
5o Outer rotor 6 Motor output shaft
6d Driver's side motor output shaft
6p Motor output shaft on passenger side
20 Cross axis reducer
20d Cross-axis reducer on driver's side
20p Cross-axis reducer on passenger side
21 Warm
21d Driver side warm
21p Passenger side warm
22 Worm wheel
22d Worm wheel on driver's side
22p Worm wheel on the passenger side
30 Gear transmission mechanism
30d Gear transmission mechanism on driver's side
30p Gear transmission mechanism on the passenger side
31 Input shaft
31d Driver's side input shaft
31p Passenger side input shaft
32 Output shaft
32d Driver's side output shaft
32p Passenger side output shaft
33 Differential gear mechanism
33d Driver side differential gear mechanism
33p Passenger side differential gear mechanism
34 Career
34d Driver side carrier
34p Passenger side carrier
35 Planetary gear (non-circular gear pair)
35d Planetary gear on driver's side (non-circular gear pair)
35p Planetary gear on the passenger side (non-circular gear pair)
36 Planetary gear (round gear pair)
36d Planetary gear on the driver's seat (circular gear pair)
36p Planetary gear on the passenger's side (round gear pair)
37 Fixed gear (non-circular gear pair)
37d Driver side fixed gear (non-circular gear pair)
37p Passenger side fixed gear (non-circular gear pair)
38 Output gear (round gear pair)
38d Driver side output gear (round gear pair)
38p Passenger side output gear (round gear pair)

Claims (18)

In a wiper drive device that swings a wiper arm via a gear transmission mechanism by a unidirectional rotating motor,
The gear transmission mechanism has an input shaft to which one-way rotation is input from the motor and an output shaft to which the wiper arm is attached arranged coaxially facing each other, and is driven to rotate between these input and output shafts. With a differential gear mechanism to combine,
A carrier rotating with the input shaft and a pair of planets attached to rotate integrally with each other around an axis parallel to the input shaft at an eccentric portion of the carrier that is radially offset from the input shaft. A compound planetary gear set comprising gears, a fixed gear meshed with one of these planetary gears and coaxially arranged on the input shaft, and an output gear meshed with the other planetary gear and secured coaxially to the output shaft,
At least one of the fixed gear side gear pair composed of the one planetary gear and the fixed gear and the output gear side gear pair composed of the other planetary gear and the output gear is a non-circular gear pair, and the pitch curve of the non-circular gear pair A wiper drive device characterized in that the moving radius is set so that the output shaft swings despite the one-way rotation of the input shaft. In the wiper drive device according to claim 1,
The motor is arranged such that the motor output shaft rotation axis has an angle of intersection with the axis of the input shaft,
A wiper drive device characterized in that a cross-axis speed reducer for transmitting rotation from the motor output shaft to the input shaft is provided at the intersection of the motor output shaft and the input shaft. In the wiper drive device according to claim 1 or 2,
The output gear side gear pair is a circular gear pair, the fixed gear side gear pair is a non-circular gear pair,
A displacement curve indicating the relationship of the rotation angle θ ₃ of the output shaft with respect to the rotation angle θ ₁ of the input shaft is a displacement curve in which dθ ₃ / dθ ₁ and d ² θ ₃ / dθ ₁ ² continuously change. A wiper drive device characterized in that a radius of a pitch curve in the non-circular gear pair is set so that the output shaft swings between a lower reverse position and an upper reverse position. In the wiper drive device according to any one of claims 1 to 3,
The output gear side gear pair is a circular gear pair, the fixed gear side gear pair is a non-circular gear pair,
By setting the radius of the pitch curve in the non-circular gear pair so that the displacement curve indicating the relationship of the rotation angle of the output shaft to the rotation angle of the input shaft becomes a sinusoidal curve with one rotation of the input shaft as one cycle. A wiper driving device characterized in that the output shaft swings between a lower inversion position and an upper inversion position of the displacement curve. In the wiper drive device according to any one of claims 1 to 4,
A displacement curve indicating the relationship of the rotation angle of the output shaft with respect to the rotation angle of the input shaft has a sine wave having different periods in a section from the lower inversion position to the upper inversion position and in an area from the upper inversion position to the lower inversion position. However, as a whole, these sine wave curves have one rotation of the input shaft as a whole, and the pitch curve in the non-circular gear pair so that it becomes a smoothly continuous curve at the lower inversion position and the upper inversion position. A wiper driving device characterized in that the moving radius of the wiper is set. In the wiper drive device according to any one of claims 1 to 5,
A pitch curve in a pair of non-circular gears so that a displacement curve indicating the relationship of the rotation angle of the output shaft with respect to the rotation angle of the input shaft becomes a curve that stops the rotation of the output shaft for a minute time at the lower and upper reverse positions. A wiper driving device characterized in that the moving radius of the wiper is set. In the wiper drive device according to any one of claims 1 to 6, used as a wiper drive device for a driver's seat side wiper, and a wiper drive device for a passenger side wiper.
A wiper drive device characterized in that a radius of a pitch curve in a non-circular gear pair is set so that a maximum swing angle of a passenger-side wiper is larger than a maximum swing angle of a driver-side wiper. In the wiper drive device according to claim 7,
The displacement curve indicating the relationship of the rotation angle of the output shaft with respect to the rotation angle of the input shaft makes the rotation stop period of the output shaft at the downward inversion position longer at the passenger seat side wiper than at the driver seat side wiper, A wiper drive device characterized in that a radius of a pitch curve in a non-circular gear pair is set so that a rotation stop period of an output shaft at a position becomes a curve that is shorter on a passenger seat side than on a driver seat side wiper. In the wiper driving device according to any one of claims 1 to 8, used as a wiper driving device for a driver side wiper, and a wiper driving device for a passenger side wiper.
The one-way rotating motor is a single motor common to the driver side wiper and the passenger side wiper,
A wiper drive characterized in that a driver-side wiper and a passenger-side wiper are drive-coupled to one output shaft of the motor via a driver-side wiper gear transmission mechanism and a passenger-side wiper gear transmission mechanism, respectively. apparatus. In the wiper drive device according to claim 9,
One motor common to the driver-side wiper and the passenger-side wiper is a motor in which both ends of the one motor output shaft project from both ends in the motor axial direction,
A wiper characterized in that a driver-side wiper and a passenger-side wiper are drivingly coupled to both ends of the projecting motor output shaft via a driver-side wiper gear transmission mechanism and a passenger-side wiper gear transmission mechanism, respectively. Drive device. In the wiper drive device according to claim 9 or 10,
The cross-axis speed reducer is composed of a driver-side worm and a passenger-side worm that are rotationally driven by the motor, and a driver-side worm wheel and a passenger-side worm wheel that mesh with these worms, respectively.
The twisting direction of the teeth of the driver side worm and the twisting direction of the teeth of the passenger side worm are the same, and the driver side wiper and the passenger side wiper are swung in the same phase. Wiper drive device. In the wiper drive device according to claim 9 or 10,
The cross-axis speed reducer is composed of a driver-side worm and a passenger-side worm that are rotationally driven by the motor, and a driver-side worm wheel and a passenger-side worm wheel that mesh with these worms, respectively.
The twisting direction of the teeth on the driver side worm and the twisting direction of the teeth on the passenger side worm are opposite to each other, and the driver side wiper and the passenger side wiper are swung in opposite phases. A wiper drive device characterized. In the wiper driving device according to any one of claims 1 to 8, used as a wiper driving device for a driver side wiper, and a wiper driving device for a passenger side wiper.
The one-way rotary motor is a composite motor having two rotors that are individually driven to rotate by magnetic coupling with one stator,
One of these rotors is drivingly coupled to the driver's seat side wiper via the driver's seat side wiper gear transmission mechanism, and the other side is connected to the passenger's seat side wiper via the passenger seat side wiper's gear transmission mechanism.
These driver-side wiper and passenger-side wiper are arranged so that the wiper blades overlap each other in the wiping direction in the non-operating position,
A wiper driving device characterized in that the swing angle of the passenger-side wiper is larger than the swing angle of the driver-side wiper. The wiper drive device according to claim 13, wherein the composite motor is a radial gap type composite motor configured by disposing an inner rotor and an outer rotor on the inner and outer circumferences of the stator, respectively.
Of the driver side wiper and passenger side wiper, the wiper with the larger wiping load is drivingly connected to the outer rotor via the corresponding gear transmission mechanism for wiper, and the wiper with the smaller wiping load is supported. A wiper drive device characterized in that it is drivingly coupled to the inner rotor via a wiper gear transmission mechanism. The wiper drive device according to claim 14,
A wiper drive device characterized in that an outer rotor and an inner rotor of the composite motor are rotated in fixed directions opposite to each other. The wiper drive device according to claim 15,
The cross-axis speed reducer is composed of a driver-side worm and a passenger-side worm that are rotationally driven by the two rotors, respectively, and a driver-side worm wheel and a passenger-side worm wheel that mesh with these worms, respectively.
The twisting direction of the teeth of the driver seat side worm and the twisting direction of the teeth of the passenger seat side worm are opposite to each other, and the driver seat side wiper and the passenger seat side wiper are configured to swing in the same phase. A wiper drive device characterized. The wiper drive device according to claim 15,
The cross-axis speed reducer is composed of a driver-side worm and a passenger-side worm that are rotationally driven by the two rotors, respectively, and a driver-side worm wheel and a passenger-side worm wheel that mesh with these worms, respectively.
The twisting direction of the teeth of the driver side worm and the twisting direction of the teeth of the passenger side worm are the same, and the driver side wiper and the passenger side wiper are swung in opposite phases. Wiper drive device. In the wiper drive device according to any one of claims 13 to 17, wherein the driving of the driver side wiper and the passenger side wiper is automatically controlled according to the raindrop amount detection value from the raindrop detection means.
According to the result of comparing the raindrop amount detection value sequentially with the first set value and the second set value that are large,
If the raindrop amount detection value is less than the first set value, both the driver side wiper and the passenger side wiper are stopped,
If the raindrop amount detection value is a value between the first set value and the second set value, the driver side wiper is operated once for the driver side wiper being operated multiple times,
If the raindrop amount detection value is equal to or greater than the second set value, the two rotors of the composite motor are driven and controlled to operate both the driver's seat side wiper and the passenger's seat side wiper without restriction. A wiper drive device characterized.

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