JPH01186448A - Wiper for vehicle - Google Patents

Abstract

PURPOSE:To adjust wiping angle freely by coupling a crank lever with a roll lever coupled to the pivot shaft of a wiper arm through a link arm, and making one of the coupling points movable corresponding to vehicle speed and the like. CONSTITUTION:A pivot shaft 41 to be secured to the base section of a wiper arm 40 is coupled to one end of the lever 71 in U-ink 70, and the pivot shaft 41 is supported on a housing secured to the front plate 2 of body through a bush 41a. Lever 72 in the U-link 70 is coupled to a shaft 91 pivoted to an eccentric shaft 92 supported on the housing 43 at the outside, then a ratchet gear, i.e. a gear plate 93, rotatable integrally with the lever 72 is contained in a recess of the flange of the eccentric shaft 92 so that notches 93a1-93a4 formed on the outer circumference thereof can engage with a pawl 100 secured to the output shaft of a motor secured to the eccentric shaft 92. The lever 72 is rolled through reciprocal motion of a crank lever 60 caused through a drive motor.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention relates to a wiper device for a vehicle, and more particularly to a wiper device with variable wiping angle.

[Prior Art] In a conventional vehicle wiper device, the wiping angle of the wiper arm is constant. In recent years, wiper devices have been installed in which the wiper arm is raised down into the cowl when the wiper is not in use, and the lower inverted position of the wiper arm is raised up near the bottom edge of the windshield only when the wiper is in use, improving the exterior design of vehicles. Even in such a wiper device, the wiping angle during operation is constant.

[Problems to be Solved by the Invention] By the way, when a vehicle is running at high speed, large wind pressure acts on the wiper arm, and there is a risk that the lower inverted position of the wiper arm on the driver's seat side may be pushed in one direction and come into contact with the pillar. .

Therefore, in the above-mentioned conventional wiper device, the wiping angle of the wiper arm is made small in advance to prevent contact between the wiper arm and the pillar during high-speed driving.
Rain visibility when driving at low speeds was sometimes slightly poor.

The present invention solves this problem, and provides a wiper device for a vehicle that can change the wiper arm wiping angle according to the running speed of the vehicle and can always obtain good rain visibility regardless of high or low speed. With the goal.

[Means for Solving the Problem] The wiper device of the present invention includes at least one crank lever that is connected to the output shaft of the drive motor and rotates, and a swing lever that is connected to the pivot shaft of the wiper arm and swings. The wiper arm is connected by a link arm, and is characterized by being provided with a moving drive means for moving one of these connection points or one of the output shaft and the pivot shaft in accordance with at least the vehicle speed and the rotational position of the wiper arm.

Also, link the above two connection points with the swing arm.
A ratchet that serves as a connection point for the arms, connects the swing arm and the link arm by an eccentric shaft, and provides the movement drive means so as to be relatively rotatable about the pivot axis with sliding resistance. A gear, a rotation transmission means for transmitting the rotation of the ratchet gear to the eccentric shaft, a pawl that engages with the ratchet gear to stop its rotation, and a pawl that engages the ratchet gear between an engaged position and a disengaged position. It is composed of a claw body moving means for moving the claw body.

Further, the two connection points are used as connection points between the swing arm and the pivot shaft, and the movement drive means is connected to an eccentric shaft provided to be relatively rotatable about the pivot shaft and to which one end of the swing arm is connected. a ratchet gear integrally installed with the eccentric shaft so as to be relatively rotatable around the pivot axis with sliding resistance; a pawl body that meshes with the ratchet gear to stop its rotation; It is comprised of a pawl body moving means for moving between an engaged position and a disengaged position.

[Operation] The above-mentioned two connection points are moved by the moving drive means,
Alternatively, if the drive motor output shaft or wiper arm pivot shaft is moved in the direction perpendicular to the axis, the relative postures of the crank lever, swing lever, and link arm change according to the amount of movement, and the pivot shaft corresponds to these posture changes. The offset rotation can be made by the amount of the angle.

Such offset rotation of the pivot shaft moves, for example, the lower reversal position of the wiper arm, thereby changing the wiping angle.

[First example] A first embodiment of the present invention is shown in FIGS. 1 to 14.

In FIG. 3, the lower side of the front window W of the vehicle 1 includes a wiper blade 10, a wiper arm 20, a wiper blade 30, a wiper arm 40, a drive motor 50, a lever crank link 60, a U link 70, a lever lever link 80, and a wiping angle. A variable mechanism 90 is provided. The position of the wiper blade in the figure is in the rise-down state, the solid line shows the lower reversed position of the rise up, the broken line shows the lower reversed position of the wiper blade, and the dashed-dotted line shows the lower reversed position of the small wiping angle.

The wiper blade 10, wiper arm 20, wiper blade 30, and wiper arm 40 have a known configuration,
The wiper arm 20 is attached to the pivot shaft 21, and the wiper arm 4
0 are fixed to the pivot shaft 41 by nuts 22 and 42, respectively.

The pivot shaft 21 is connected to the lever 8 of the lever lever link 80.
The lever 81 is connected to the lever 71 of the U-link 70 by a rod 82.

This will be explained in detail below with reference to FIGS. 1, 2, and 4 to 6.

The pivot shaft 41 rotates together with a lever 71 of the U link 70, and the lever 71 is connected to a lever 72 by a rod 73. Further, the pivot shaft 41 is attached to a bushing 41a in a housing 43 which is fixed to the top plate 2 of the vehicle body 1 with screws 3.
An oil reservoir 41b is formed between the pivot shaft 41 and the housing 43. A washer 41d and a clip 41e are fitted into the protrusion 41c of the pivot shaft 41 from the housing 43, and the pivot shaft 41 is prevented from being removed from the housing 43.

The pivot shaft H is supported in the same manner as the pivot shaft 21.

The lever 72 is connected to the support shaft 91 and rotates together. The support shaft 91 is an eccentric shaft 9 that is pivotally supported on the outside by the housing 43.
It is supported by 2.

The lever 7 is attached to the four parts 92b of the flange 92a of the eccentric shaft 92.
A gear plate 93 as a ratchet gear that rotates integrally with the gear plate 2 is provided. A movable contact 94 shown in FIG. 8 is fixed to the gear plate 93, and fixed contacts 95a, 95b, 9 are etched on the printed circuit board 95 shown in FIG.
5c, 95d, and 95e are provided. The arm 94a of the movable contact 94 constantly slides on the fixed contact 95a.
4b slides on fixed contacts 95b and 95c, and arm 94c slides on fixed contacts 95d and 9Se, respectively.
The relative position of the lever 72 and the eccentric shaft 92 can be detected by the presence or absence of resistance between the fixed contacts 5b to 95e and the fixed contact 95a.

A washer 96 and a clip 97 are attached to one end 91a of the support shaft 91.
are fitted, and the support shaft 91 and eccentric shaft 92 are attached to the housing 43. Cap 98 prevents foreign matter from entering the bearing. A stepped portion 91b for an oil reservoir is provided at the center of the support shaft 91.

Further, the eccentric shaft is also provided with a stepped portion 92C for an oil reservoir.

Notches 93a1 to 93a are provided on the outer periphery of the gear plate 93.
4 is engraved on the right end 100b or left end 1 of the claw 100, which is fixed to the output shaft 99a of the motor 99 fixed to the flange 92a of the eccentric shaft 92 via an elastic body 100a.
Can mesh with 00c.

Three four portions 92d are arranged on the outer periphery of the eccentric shaft 92, each corresponding to a fixed contact position.

Since the ball 101b pushed out by the spring 101a built in the ball plunger 101 fixed to the housing 43 is housed in the recess 92d, the eccentric shaft 92 will not rotate unless a given constant torque or more is applied to the eccentric shaft 92.

With the above configuration, this device operates as follows.

Normally, when the drive motor 5.0 rotates, the lever 72 swings via the lever and crank link, the lever 71 swings via the U link 70, and the lever 81 swings via the lever link 80. . At this time, Figure 1.0, Figure 11
As shown in the figure, when the eccentric shaft 92 is rotated by Qex degrees with reference to an arbitrary position, the lever 71, the lever 72, and the rod 73 move from the position shown by the broken line to the position shown by the solid line. As a result, the downward inversion position changes by 60 degrees, and the downward inversion position changes by 60 degrees.

FIG. 12 is a graph of this relationship.

The horizontal axis represents the rotation angle θex with respect to an arbitrary position where the eccentric shaft 92 is located, and the vertical axis represents the upward or downward inversion position change angle. By making good use of this characteristic, it is possible to determine the rise-down position, rise-up position, lower reversal position at a negative wiping angle, and lower reversal position at a small wiping angle.

For example, if the eccentric shaft rotation angle is C degrees, the lower inversion position change angle is -θdc degrees. If the rotation angle of the eccentric shaft is b, the angle of change in the lower inversion position is +θdab degree, and the angle of change in the lower inversion position is +
θub degrees. If the rotation angle of the eccentric shaft is a, the change angle of the lower inversion position is +θdab degree, and the change angle of the lower inversion position is +θU.
It will be a degree. To summarize the above, the amount of rise up is (
10 θdab −(−θdc))=Qdab+θdc degrees,
The difference between the downward inversion position of the wiping angle small and the wiping angle small is (θab - θU
a) Degree. Note that the lower reversal positions of the wiping angle small and the wiping angle small are the same.

Furthermore, the positive and negative values of each reversal position change angle are positive in the counterclockwise direction of the wiper arm when viewed from the front of the vehicle.

The actual operation is as follows.

The position of the eccentric shaft 92 is changed as follows. Fourth
Operate from the state shown in the figure. The figure shows the rise down condition.

In the figure, the lever 72 begins to rotate counterclockwise (θex=c degrees). After detecting that the contacts 95d and 95a are closed, when the motor 99 is turned on and the pawl 100 is rotated clockwise in the figure, the right end 100b of the pawl 100 will soon engage the notch 93a1 of the gear plate 93. Fit. Since a torque greater than the sliding resistance by the ball plunger 101 is applied to the eccentric shaft 92, the eccentric shaft 92 rotates together with the gear plate 93.

When the lever 72 reaches the inverted position, the rotation angle of the eccentric shaft 92 becomes b degrees. At this time, the lower reversal position change angle is +θab degrees, which is a negative dog. Also, at this position = 11 -, the ball plunger 101 is again inserted into the recess 92 of the eccentric shaft 93.
Fits with d.

After this, when the lever 72 begins to rotate clockwise, the claw 1
The right end 100b of 00 is pushed out to the outer peripheral end of the gear plate 93, and the claw 100 and the gear plate 93 are disengaged.

Further, the lever 72 rotates and returns to the inverted position.

At this time, the lower reversal position change angle is +θdab, which is the rise-up position.

The lever 72 begins to rotate counterclockwise, and the contact 95e
After detecting that 95a is closed, the motor 99 is turned on and the pawl 100 is rotated clockwise in FIG. . Since a torque greater than the sliding resistance by the ball plunger 101 is applied to the eccentric shaft 92, the eccentric shaft 92 rotates together with the gear plate 93.

When the lever 72 reaches the inverted position, the rotation angle of the eccentric shaft 92 is a degree, and the lower inverted position change angle is +θUa degree,
The wiping angle is small. At this position, the ball plunger 10 again fits into the recess 92d of the eccentric shaft 93.

After this, when the lever 72 begins to rotate clockwise, the claw 1
The right end 100b of 00 is pushed out to the outer peripheral end of the gear plate 93, and the claw 100 and the gear plate 93 are disengaged.

Further, the lever 72 rotates and returns to the inverted position. At this time, the lower reversal position change angle is +θdab, which is the rise-up position.

The lever 72 rotates counterclockwise, and after reversing, begins to rotate clockwise. After detecting that the contacts 95a and 95c close, turn on the power to the motor 9a and rotate the pawl 100 counterclockwise in the figure, and the left end 100c of the pawl 100 will soon meet the notch 93a3 of the gear plate 93. mesh together. Since a torque greater than the sliding resistance by the ball 1 langeer 101 is applied to the eccentric shaft 92, the eccentric shaft 92 rotates together with the gear plate 93.

When the lever B72 reaches the reversal position, the rotation angle of the eccentric shaft 92 becomes b degrees again, and the lower reversal position change angle is +θdab, which is the rise-up position. Also, at this position, the ball plunger 101 is fitted into the recess 92d of the eccentric shaft 93 again.

After this, when the lever 72 begins to rotate counterclockwise, the left end 100C of the pawl 100 is pushed out to the outer peripheral edge of the gear plate 93, and the pawl 100 and the gear plate 93 are disengaged.

Further, the lever 72 rotates and returns to the inverted position. At this time, the angle of change of the lower reversal position is θub, which is a negative dog.

After detecting that the lever 72 begins to rotate clockwise and the contacts 95b and 95a close, the motor 99 is turned on and the pawl 100 is rotated counterclockwise in FIG. The left end 100c of the gear plate 93 meshes with the notch 93a4 of the gear plate 93, and since a torque greater than the fixing force of the ball plunger 101 is applied to the eccentric shaft 92,
Eccentric shaft 92 rotates together with gear plate 93.

When the lever 72 reaches the inverted position, the rotation angle of the eccentric shaft 92a becomes 0 degrees again, and the lower inverted position change angle is 1θdc.
degree and the rise down position.

In this position, the ball plunger 101 is again connected to the eccentric shaft 92.
It fits with the fourth part 92d.

The eccentric shaft 93 is formed by the claw 101 and the notches 93 to 93a4.
will have three stopping positions relative to the housing 43.

Here, the load that the claw 101 receives from the gear plate 93 is:
An elastic body 1 is placed between the claw 101 and the output shaft 99a of the motor 99.
00a, when the elastic body 100a is bent, the wall 9 in the four parts 92d of the flange 92a of the eccentric shaft 92
Take it at 2e. Therefore, no excessive load is applied to the output shaft 99a of the motor 99.

By controlling the operation of the motor 99 according to the vehicle speed and wiper switch settings, it is possible to raise and lower the wiper arm and change the lower reverse position.

An example of control is shown in FIGS. 13 and 14.

FIG. 13 shows a control block diagram. Signals from a known stop position detection sensor 52 built into the drive motor 50, a wiper switch 53, a vehicle speed sensor 54, and a position sensor 55 of the eccentric shaft 92 are input to the control circuit #I51. Control circuit 51 processes these signals to control drive motor 50 and motor 99.

The control procedure will be explained with reference to the flowchart in FIG. The processing and judgment in each step in the figure are as follows.

5101: Does nothing if wiper switch WPS/W is OFF. If it is other than OFF, proceed to 5102.

5102. Let CT=O.

8103; If the wiper switch is set to High motor or the vehicle speed is Vkm/h or more, proceed to 8123; otherwise proceed to 5104.

8104; If the wiper switch is not OFF, proceed to 5114 from OFF to 8105.

5105. CT=1 to 8111 otherwise 81
Proceed to 06. - 8106, 5107 if contact 95b and contact 95a are closed
If not, return to 8103.

5107 to 5109, after continuing to rotate the motor 99 in the counterclockwise direction for T1 time, the motor 99 is stopped.

Sl 10, stop the motor 50 at the stop position.

5i11. If the contacts 95c and 95a are closed, the process returns to 5112; otherwise, the process returns to 8103.

5112-8113. Turn motor 99 counterclockwise
After rotating for 2 hours, proceed to 5106.

8114; If CT=2, return to 5103; otherwise, proceed to 5115.

5115; If CT=1, proceed to 5119; otherwise, proceed to 8116.

5116. If the contacts 95d and 95a are closed, the process proceeds to 5117; otherwise, the process returns to 8103.

5117-5118; Motor 99 clockwise T3
After time rotation, the process advances to 5122.

5119. If the contacts 95c and 95a are closed, the process proceeds to sl20; otherwise, the process returns to 8103.

5120.121; After rotating the motor 99 counterclockwise for T2 time, proceed to 5122.

5L22. Return to CT=2 binding 8103.

3123, if CT=1, return to 8103, otherwise proceed to 5124.

5124, if CT=2, proceed to 5129; Otherwise, proceed to 5125.

5125, if the contacts 95d and 95a are closed, the process returns to 5126; otherwise, the process returns to 8103.

5126.127; After rotating the motor 99 clockwise for T3 time, proceed to 5128.

5128. Set CT=2 and proceed to 5129.

8129; 81' if contacts 95e and 95a are closed
30, otherwise return to 8103.

5130.5131. Turn motor 99 clockwise T4
After rotating the time, proceed to 5132nd floor.

8132, CT=1 binding and return to 8103.

Due to the mechanism, action, and control content explained above,
This device is in the rise down position (S105 to 5113) when the wiper is stopped, and when the wiper is in intermittent or constant speed operation (Int, Low), the wiper is wiped at the vehicle speed below Vkm/h (8114 to 5122), and the wiper is in high speed operation. Time (H
igh) or at a vehicle speed of V km/h or higher
123 to 8131).

Hereinafter, the control contents for the second embodiment and the subsequent embodiments will not be particularly explained because they can be designed using known techniques according to FIG. 14.

[Second example] A second embodiment of the invention is shown in FIG.

In the first embodiment, the claw 10 is used to rotate the eccentric shaft 92.
0 and notches 93a1 to 93a4, but in this embodiment, a helical gear 193a is provided on the eccentric shaft 193, and a worm 194 that meshes with the helical gear 193a is rotated by a motor 195. Eccentric shaft 1
Rotate 93.

The rotation angle of the eccentric shaft 193 is determined by counting pulses generated by a pulse generator attached to the rear end of the motor 195.

[Third Embodiment] A third embodiment of the present invention will be described using FIGS. 16 to 20.

In the first and second embodiments, the spindle was moved using an eccentric shaft, but in the third embodiment, the spindle was moved using a screw nut.

Further, in this embodiment, the wiping angle can be changed only on the driver's seat side. Of course, like the first and second embodiments, it can also be installed on the passenger seat side.

The wiper arm '310 is fixed to a pivot shaft 320 by a nut 311.

The pivot shaft 320 is fixed to a lever 331 of a U-link 330 and is pivotally supported by a housing 340 fixed to the top plate 2 of the vehicle body 1.

Lever 331 is connected to lever 333 via rod 332.

Lever 333 is pivotally supported by lever 350.

The lever 350 is the support shaft 3 of the lever 333 and the rod 332.
32a, and is pivotally supported by a support shaft 351 on the housing 340.

-20- A pin 371 protruding from a nut 370 that moves with the rotation of a screw 361 driven by a motor 360 fixed to the top plate 2 slides into an elongated hole 352 provided at one end of the lever 350. It is possible. Also, lever 350
The position of is known by counting the output pulses of the pulse generator 362 on the rear side of the motor 360.

The above configuration results in the following operation.

When the motor 360 is rotated to move the nut 370, the lever 350 rotates around the support shaft 351. The link relationships at this time are shown in FIGS. 18 and 19.

FIG. 18 shows a state in which the lower inversion position has changed, and FIG. 19 shows a state in which the lower inversion position has changed.

In FIG. 18, when the lever 350 rotates, it means that the lever 333 rotates at a radius R around the support shaft 332a. Therefore, lever 3
31 does not move at all. That is, the lower inversion position change angle is always zero even if the lever 350 is rotated.

In FIG. 19, when the lever 35o (FIG. 17) rotates, the state shown by the broken line changes to the state shown by the solid line.

The above relationship is shown in FIG. The horizontal axis is the rotation angle of the lever 350, and the vertical axis is the downward inversion position change angle θU.

Therefore, this device can continuously change only the lower inversion position without changing the lower inversion position.

[Fourth Example] A fourth example of the present invention will be described using FIGS. 21 to 25.

In the third embodiment, the lever 333 was moved along the radius R, but in this embodiment, the lever 333 is moved on a tangent to the radius R.

The lever 433 is a nut 4 that moves with the rotation of a screw 461 driven by a motor 460 fixed to the top plate 2.
It is pivotally supported by a pin 471 that protrudes from 70.

The pin 471 is the support shaft 43 of the lever 433 and the rod 432.
It moves on the tangent of a circular arc of radius R centered at 2a.

The link relationships at this time are shown in FIGS. 3 and 24. Second
FIG. 3 shows a state in which the lower inversion position has changed, and FIG. 24 shows a state in which the lower inversion position has changed. Further, the characteristics are shown in FIG. 25, where the horizontal axis is the amount of movement of the lever 433, and the vertical axis is the lower inversion position change angle θU and the lower inversion position change angle θd.

The lower reversal position change angle θd is not a circular arc as in the third embodiment but is a tangent line, so it is not completely zero, but it can be used sufficiently.

The lower inversion position change angle θU is the same as in the third embodiment. This embodiment is a cost reduction version of the third embodiment.

[Fifth Example] A fifth example of the present invention will be described using FIGS. 26 to 29.

In the third and fourth embodiments, the support shaft was moved along an arc or a straight line, but in this embodiment, it can be moved along an arbitrary curve.

The lever 533 is connected to a motor 56 fixed to the lever 550.
It is pivotally supported by a pin 571 that protrudes from a nut 570 that moves with the rotation of a screw 561 driven to zero. The lever 550 is pivotally supported on the top plate 2 by a shaft 551. An elongated hole 552 is provided at the other end of the lever 550, and a pin 591 that protrudes from a nut 590 that moves with the rotation of a screw 581 driven by a motor 580 fixed to the top plate 2 slides into the elongated hole 552. It is movable. By adopting the above configuration, the position of the rotation center shaft 571 of the lever 533 can be moved to an arbitrary position by the operation of the motor 560 and the motor 580.

For example, the spindle 571 of the lever 533 is driven by the motor 560.
It is possible to move the lever in a straight line as in the fourth embodiment, usually change only the lower inversion position, and rotate the support shaft 571 of the lever 533 around the support shaft 551 by the motor 580 to provide a rise-up function. I can do it.

FIG. 28 shows the lower inverted position state. The broken line is the rise-down position, and the solid line is the rise-up position.

FIG. 29 shows the amount of change in the lower reversal position θU and the lower reversal position θd when only the motor 560 is operated from the rise-up position.

[Sixth Embodiment] A sixth embodiment of the present invention will be described using FIGS. 30 to 33.

In the fifth embodiment, two motors were used to freely move the support shaft, but in this embodiment, one motor is used to freely move the support shaft.

The lever 633 is connected to a motor 66 fixed to the lever 650.
It is pivotally supported by a pin 671 that protrudes from a nut 670 that is driven to zero and moves as the screw 661 rotates.

On the other hand, a pin 672 which is coaxial with the pin 671 and protrudes in the opposite direction from the nut 670 passes through an elongated hole 652 provided at the other end of the lever 650, which is supported on the top plate 2 by a shaft 651, and is further inserted into the top plate 2. It is slidably housed in a fixed cam groove 653. Therefore, when the motor 660 operates, the lever 6
The support shaft 671 of No. 33 moves along the cam groove 653. The cam groove 653 is a cam groove 653a that changes the lower inversion position.
and a cam groove 653b that changes the lower inversion position.

FIG. 32 shows the lower inversion position change state, that is, the cam groove 653
This shows when the pin 672 moves within a.

The broken line is before movement, and the solid line is after movement.

FIG. 33 shows the amount of change in the upper and lower inversion positions when the pin 672 moves within the cam groove 653b. It can be seen that only the bottom inversion position changes.

[Seventh Example] A seventh embodiment of the present invention is shown in FIGS. 34 to 41.

In the first to sixth embodiments, a lever was added to the middle of the rod and the supporting shaft of the lever was moved, whereas in this embodiment, the pivot shaft that fixes the wiper arm is moved to change the wiping angle.

In FIG. 34, a wiper blade 710, a wiper arm 720, a wiper blade 730, a wiper arm 740, a drive motor 750, a lever crank link 760, a lever lever link 770, and a variable wiping angle mechanism 780 are attached to the lower side of the front window W of the vehicle 1. will be established. The broken lines indicate the wiping surfaces of the wiper blades 710 and 730, and the dashed-dot line indicates the lower inverted position where the wiping surface of the wiper blade 710 becomes smaller.

This will be explained in detail using FIGS. 35 to 38.

The wiper arm 720 has a fixed member 721 with a shaft 721a,
A link 722 that is pivotally supported by bushes 721b and 721c, and a rivet 722a that is caulked to the link 722.
It consists of a wiper rod 723 fixed at. or,
A wiper blade 710 is attached to the tip of the wiper rod 723.
is attached with screws, etc.

The contact pressure spring 725 has one end attached to the wiper rod 723.
The other end is suspended by a pin 721a fixed to the fixing member 721 in the hole 723a, and acts as a spring member to generate the necessary contact pressure between the wiper blade 710 and the window W surface.

On the other hand, a fixing member 721 of the wiper arm 720 is fixed by a screw 727 to the tip of a pivot shaft 726 which swings through a lever crank link 760 and a lever lever link 770 as the drive motor 750 rotates. The pivot shaft 726 is attached to a screw 729 on the vehicle top plate 2.
The gear plate 737 is pivotally supported on an eccentric shaft portion 737a of a gear plate 737, which is pivotally supported on a housing 730 fixed by a washer 731 and a clip 732, and rotatably supported on the housing 730. Also, an oil reservoir 737b is provided on the eccentric shaft portion 737a of the gear plate 737, and an oil reservoir 737b is provided on the eccentric shaft portion 737a of the gear plate 737.
26 is provided with an oil reservoir 726a.

A cover 73 is provided around the protrusion 726b of the pivot shaft 726.
8 is rotatably attached.

Since the pivot shaft 726 receives the frictional force of the shoe 7370 by the spring 737b provided in the gear plate 737, the pivot shaft 726 and the gear plate 737 will not move unless static torque of a certain value or more is applied to the gear plate 737. Rotates as one.

A notch 737 is provided on the outer periphery of the flange portion of the gear plate 737.
d-1 and 737d-2 are provided. Notch 737d
-1, 737d-2 can be engaged with a pawl 742 provided near the gear plate 737.

The claw 742 is attached to an output shaft 743a of a small motor 743 fixed to the housing 730 via an elastic body 742a.

The claw 742 and the notches 737d-1 and 737d-2 are designed to engage with each other at any fixed position. For example, in FIG. 38, when the pawl 742 continues to rotate clockwise and the swing lever 761 is rotated counterclockwise, the left end 742b of the pawl 742 engages with the notch 737d-1. Then, the gear plate 737 comes to rest, and the gear plate 737 and the pivot shaft 726 cause relative rotation. When the swing lever 761 reaches the reverse position and starts rotating clockwise, the claw 74
The left end 742b of the claw 742b is pushed out of the notch 137d-1 by the outer peripheral end of the gear plate 737, and the left end 742b of the claw and the notch 737d-1 are disengaged from each other. The same relationship as above is between the clawed end 742C and the notch 737-29-
This also occurs in d-2, but here the rotation direction is opposite.Here, the load that the claw 742 receives from the gear plate 737 is due to the elastic body 742a between the claw 742 and the output shaft of the motor 743.
Since the elastic body 742a is bent, it is received by the inner wall 730a of the housing 730. Therefore, motor 7
No excessive load is applied to the output shaft 743a of No. 43.

In this embodiment, there is a two-stage changeover of no rise down, wiping negative dog, and wiping fishing hand.

With the above configuration, this device operates as follows.

Normally, when the drive motor 750 rotates, the swing lever 761 swings via the lever crank link 760 and the lever lever link 770. At this time, as shown in FIGS. 39 and 40, when the eccentric shaft portion 737a (FIG. 37) is rotated by θex degrees, the swing lever 76
1. The wiper arm 710 moves from the position shown by the broken line to the position shown by the solid line.

As a result, the lower inversion position changes by 60 degrees and the lower inversion position changes by 66 degrees. A graph of this relationship is shown in FIG. The horizontal axis represents the angle θex of rotation of the eccentric shaft portion 737a with respect to a certain arbitrary position, and the vertical axis represents the upward or downward inversion position change angle. Utilizing this characteristic, the upper reversal position of the wiper and the lower reverse position of the wiper can be determined.

For example, if the rotation angle of the eccentric shaft portion 737a is a degree, the lower inversion position change angle is +θda degrees, and the lower inversion position change angle is +θ
It becomes Ua degree. If the rotation angle of the eccentric shaft portion 737a is b degrees, the lower inversion position change angle is +θdb degrees, and the lower inversion position change angle is −θub degrees. Therefore, to summarize the above, the bottom inversion position is the same, and only the bottom inversion position is (θUa+θub)
It can be seen that the degree changes.

The actual operation is as follows.

The position of the eccentric shaft portion 737a is changed as follows. Operate from the state shown in FIG. 38. The figure shows the lower inverted position of the wiper.

In the figure, the lever 761 begins to rotate counterclockwise (θeX=a degrees). When the motor 743 is powered on and the pawl 742 is rotated clockwise in FIG. 38, the left end 742b of the pawl 742 soon engages with the notch 737d-1 of the gear plate 737. The eccentric shaft portion 737a has
Since a force greater than the friction torque of the shoe 737c (Fig. 37) is applied, the eccentric shaft portion 737a remains stationary and the pivot shaft 7
Only 26 rotates.

When the lever 761 reaches the reverse position, the eccentric shaft portion 737a
The rotation angle is b degrees. At this time, the downward inversion position change angle is
-θub degree, and it is a wiping fishing hand.

After this, when the lever 761 begins to rotate clockwise, the left end 742b of the claw 742 is pushed out to the outer peripheral end of the gear plate 737, and the engagement between the claw 742 and the gear plate 737 is disengaged.

Further, the lever 761 rotates and returns to the inverted position. At this time, the lower reversal position change angle is +θdb degrees.

After the lever 761 rotates further and reaches the lower reversal position, it begins to rotate clockwise. Turn on the power to the motor 99 and continue rotating the claw 742 clockwise. Soon, the right end 742C of the claw 742 will be connected to the notch 73 of the gear plate 737.
7 Engages with d-2.

Since a force greater than the frictional torque received from the shoe 737c is applied to the eccentric shaft portion 737a, the eccentric shaft portion 737a remains stationary and only the pivot shaft 726 rotates.

When the lever 761 reaches the reverse position, the eccentric shaft portion 737a
The rotation angle is a degree, and the lower inversion position change angle is θda degrees.

After this, when the lever 761 begins to rotate counterclockwise,
The right end 742c of the claw 742 is pushed out to the outer peripheral end of the gear plate 737, and the engagement between the claw 742 and the gear plate 737 is disengaged.

When the lever 761 further rotates and returns to the inverted position, the lower inverted position change angle is θUa degrees, which is a zero point.

[Eighth Example] An eighth embodiment of the present invention is shown in FIGS. 42 to 46.

A fixing member 821 of the wiper arm 820 is fixed to the tip of the swinging pivot shaft 826 by a screw 827. The pivot shaft 826 is pivotally supported by a housing 830 fixed to the vehicle top plate 2 with screws 829.

A fixed lever 771 is fixed to the lower end of the pivot shaft 826 and rotates together.

Recessed portion 830b of flange portion 830a of housing 830
Inside is a gear plate 83 that is pivotally supported by a pivot shaft 826.
7 has been paid.

The eccentric shaft portion 837a of the gear plate 837 is not eccentric with respect to the movable lever 772, which is a swing lever, and the pivot shaft 826 passes through the eccentric shaft portion 837a at an eccentric position.

A pin 771a protruding from the fixed lever 771 is housed in an elongated hole 772a provided in the center of the movable lever 772 and is slidable therein.

Therefore, relative rotation of the gear plate 837 with respect to the pivot shaft 826 causes relative movement between the fixed lever 771 and the movable lever 772.

As a result, the relationship between the rotation angle θex of the gear plate 837 from a certain arbitrary position with respect to the pivot shaft 826, the lower reversal position change angle θU, and the lower reversal position change angle θd is as shown in FIG.

For example, when θeX=a, θd−θda, θU=θU
When a, θex = b, θd - θdb, θU = θ
ub1, the lower inverted position is the same, and only the lower inverted position (θ
Ua-θub) degree can be changed.

Relative rotation of the gear plate 837 with respect to the pivot shaft 826 is controlled by notches 837d-1 and 837d-2 carved on the outer periphery of the flange portion of the gear plate 837, as in the seventh embodiment.
This can be done by using a claw 842 attached to an output shaft 843a of a motor 843 fixed to the housing 830 via an elastic body 742a.

[Ninth Embodiment] FIG. 47 shows a ninth embodiment of the present invention. The ninth embodiment differs from the eighth embodiment in that a pin 77 protruding from a fixed lever 771
The only difference is the sliding position of the movable lever 772, and the other configurations and operations are the same as those of the eighth embodiment.

[10th Example] A tenth embodiment of the present invention is shown in FIGS. 48 to 52.

In the eighth and ninth embodiments, an eccentric shaft was provided between the swing lever and the pivot shaft, but in the tenth embodiment, an eccentric shaft was provided between the swing lever and the link rod.

A case 1071 that also serves as a swing lever is fixed to the lower end of the pivot shaft 1026 and rotates together.

Recess 103 in flange 1030a of housing 1030
A gear plate 1037 that is pivotally supported by the pivot shaft 1026 is housed in 0b. The gear plate 1037 is
Notches 1037d-1, 1 that engage with claws 1042 driven by a motor 1043 fixed to the housing 1030
It consists of a ratchet gear part 1037a and a spur gear part 1037b having 037d-, 2.

Idle gear 1072 is pivotally supported by case 1071 and meshes with spur gear 1037b of gear plate 1037. Output gear 1073 is pivotally supported by case 1071 and meshes with idle gear 1072.

One end of the output gear 1037 passes through the case 1071 and rotates together with the eccentric shaft 1074. Eccentric shaft 1074 pivotally supports rod 1075.

In normal operation, the eccentric shaft 1074 rotates integrally with the case 1071. That is, the gear plate 1037 rotates together with the pivot shaft 1026.

When changing the wiping angle, as in the seventh embodiment, the notch 103
7d-1, 1037d-2 and the pawl 1042 engage with each other, thereby making use of the swinging force.

Further, the relationship between the rotation angle of the eccentric shaft 1074, the lower inversion position change angle, and the lower inversion position change angle at this time is the same as in the eighth embodiment.

[Eleventh Example] An eleventh embodiment of the present invention is shown in FIGS. 53 to 57.

This embodiment is obtained by adding an arm pressure variable mechanism to the seventh embodiment. Since the variable wiping angle mechanism is exactly the same as in the seventh embodiment, the variable arm pressure mechanism will be described below.

The wiper arm 1020 has a shaft 102 attached to a fixed member 1021.
1a, Push...: A link 1022 pivoted at t1021b and 1021c, and a wiper rod 1 fixed to the link 1022 by caulking and a rivet 1022a.
Consists of 023. Further, a wiper plate is attached to the tip of the wiper rod 1023 with screws or the like.

The lever 1024 has a shaft 1021a and a bush 1021b.
, 1021c, and coaxially supported with the link 1022. The contact pressure spring 1025 has one end suspended in the hole 1023a of the wiper rod 1023 and the other end suspended in the hole 1024a of the lever 1024, and acts as a spring member to generate the necessary contact pressure between the wiper blade and the window W surface. do.

Around the protrusion 1026b of the pivot shaft 1026, there is a fifth
A cam plate 1038 shown in FIG. 7 is rotatably attached.

cam play) 1038, washer 1031, and boss portion 1037a of gear plate 1037 are
They are connected by a pin 1039 (FIG. 55) that passes through them, and they always rotate together.

An end cam 1038a is formed on the cam plate 1038. Typically, the lever 1024 is under the force of a contact pressure spring 1025, and the rear end 1024 of the lever 1024 is
24a is pressed against the end cam 1038a via a locking member 1041 made of an elastic body and attached with a screw 1040.

The end cam 1038a includes a moving surface 1038b for rotating the lever 1024, and a groove 1038c that fits into the notch 1041'a of the locking tool 1041 at the stop position. Therefore, as the cam plate 1038 rotates around the pivot shaft 1026, the end cam 103
8a rotates lever 1024. Also, Notsuchi 104
1a and the groove 1038c, the cam plate 1038 will not rotate around the pivot shaft 1026 unless a predetermined torque or more is applied.

Next, the operation will be explained.

FIG. 53 to FIG. 55 show the state in which the arm is in the downward inversion position with the arm pressure lowered.

Lever 1061 begins to rotate counterclockwise.

(Fig. 41 θeX = a degree). Immediately after power is applied to the motor 1043, the eccentric shaft portion 1037a comes to rest, and only the pivot shaft 1026 rotates. At this time, the locking tool 1
041 is disengaged from the groove 1038c, and the notch 1041a slides on the moving surface 1038b. Therefore, the lever 1024 rotates and the arm pressure increases.

When the lever 1061 reaches the reverse position, the eccentric shaft portion 103
The rotation angle of 7a is θex=b degrees in FIG. 41, and the angle of change of the lower reversal position is 1 θub degrees, which is a sweeping angle. At this time, the notch 1041a again engages with the groove 1038c.

After this, when the lever 1061 begins to rotate clockwise,
The eccentric shaft portion 1037a and the pivot shaft 1026 rotate together, and both the arm pressure (high) and the wiping angle (small) are constant.

Further, the lever 1061 rotates and returns to the inverted position. At this time, the lower reversal position change angle is 10 Qdb degrees.

The lever 1061 rotates further and reaches the downward inversion position -4〇
− It then begins to rotate clockwise. motor 1043
As soon as the power is turned on, the eccentric shaft portion 1037a stops and only the pivot shaft 1026 rotates. At this time, the engagement between the notch 1041a of the locking tool 1041 and the groove 1038c is simultaneously released, and the notch 1041a slides on the moving surface. Therefore, the lever 1024 rotates and the arm pressure decreases.

When the lever 1061 reaches the reverse position, the eccentric shaft portion 1037
The rotation angle of a is again θeX=a degrees in FIG. 42, and the lower inversion position change angle is θda degrees.

At this time, the notch 1041a engages with the shaft 1038 again.

Thereafter, when the lever 1061 begins to rotate counterclockwise, the eccentric shaft portion 1037a and the pivot shaft portion 1026 rotate together, and the arm pressure (low) and wiping angle (small) are constant.

In the seventh embodiment and the eighth embodiment, the pivot shaft 7
By using 26.826 as the drive motor output shaft,
It is obvious that the wiping angle can be varied by moving the spindle position of the drive motor output lever, which is the crank lever.

It is clear that by using the pivot shaft 1026 as the drive motor output shaft in the tenth embodiment, the wiping angle can be varied by moving the position of the support shaft between the drive motor output lever and the rod.

In the first embodiment and the like, the switching is performed using a notch, a pawl, and a motor that rotates the pawl, but it is obvious that the same effect can be obtained by using other known ratchet mechanisms.

[Effects of the Invention] Thus, according to the vehicle wiper device of the present invention, the wiping angle of the wiper arm can be freely changed; for example, the wiping angle can be made large when driving at a constant speed, and made small when driving at high speed. This makes it possible to prevent contact between the wiper arm and the front pillar when driving at high speeds, while also ensuring good visibility when driving at low speeds.

[Brief explanation of the drawing]

1 to 14 show a first embodiment of the present invention, FIG. 1 is a partial cross-sectional view of the main part, and a cross-sectional view taken along the line B-B of FIG. 2, FIG. 2 is a plan view of the main part, Figure 3 is a plan view of the vehicle windshield section equipped with a wiper device, and Figure 4 is A-A in Figure 1.
5 is a partial sectional view taken along the line C-G in FIG. 2, FIG. 6 is a partial sectional view taken along the line D-D in FIG. 4, and FIG. 7 is a partial sectional view taken along the line C-G in FIG. A plan view, FIG. 8 is a perspective view of the movable contact, FIG. 9 is a sectional view of the ball plunger, and FIG. 10 is a perspective view of the movable contact.
Figures 11 and 11 are diagrams showing the lower inversion position and changes in the lower inversion position, respectively, Figure 12 is a characteristic diagram of changes in the inversion position according to the rotation angle of the eccentric shaft, and Figure 13 is a block diagram of the control section. FIG. 14 is a control flowchart, FIG. 15 is a partial sectional view of main parts showing a second embodiment of the present invention, and FIGS.
0 shows a third embodiment of the present invention, FIG. 16 is a partial sectional plan view of the main part, FIG. 17 is a partial sectional side view of the main part, and FIGS. 18 and 19 are the lower inverted position and the lower inverted position, respectively. FIG. 20 is a diagram showing the change in the reversing position according to the lever rotation angle, FIGS. 21 to 25 show the fourth embodiment of the present invention, and FIG. 21 is a plan view of the main part. , Fig. 22 is a cross-sectional side view of the main part, = 43 - Fig. 23 and Fig. 24 are diagrams showing no changes in the lower inverted position and the lower inverted position, respectively, and Fig. 25 shows the inverted position according to the lever rotation angle. FIG. 26 to FIG. 29 show the fifth embodiment of the present invention, FIG. 26 is a plan view of the main part, FIG. 27 is a cross-sectional side view of the main part, and FIG. 28 is a lower inverted position. FIG. 29 is a characteristic diagram of changes in the reversal position according to the lever shaft movement amount, FIGS. 30 to 33 show the sixth embodiment of the present invention, and FIG. 30 is a plan view of the main part. Fig. 31 is a cross-sectional side view of the main part, Fig. 32 is a diagram showing changes in the lower reversal position, Fig. 33 is a characteristic diagram of changes in the reversal position according to the amount of pin movement, and Figs. 34 to 41 34 shows a seventh embodiment of the present invention, FIG. 34 is a plan view of a vehicle windshield provided with a wiper device, FIG. 35 is a plan view of a wiper arm, FIG. 36 is a partially sectional side view thereof, and FIG. 37 is a cross-sectional side view of the main part, FIG. 38 is a cross-sectional plan view of the main part, and FIGS. 39 and 40 are
The figures show the changes in the lower inverted position and the lower inverted position, respectively. Figure 41 is a characteristic diagram of changes in the inverted position according to the rotation angle of the eccentric shaft portion. Figures 42 to 46 show the eighth embodiment of the present invention. An example is shown in FIG. 42, which is a partial cross-sectional side view of the wiper arm;
43 is a sectional view taken along the line E-F in FIG. 42, FIG. 44 is a sectional view taken along the line GG in FIG. 43, and FIG.
46 is a characteristic diagram of the change in the reversal position according to the rotation angle of the eccentric shaft portion, and FIG. 47 is a partial cross-sectional plan view of the main part showing the ninth embodiment of the present invention. , Fig. 48 to Fig. 52 show a tenth embodiment of the present invention, Fig. 48 is a plan view of the main part, Fig. 49 is a partial sectional view taken along line J'-J in Fig. 48, and Fig. 50. is a sectional view taken along line H-H in FIG. 48,
51 is a cross-sectional view taken along the line L--L in FIG. 49, FIG. 52 is a cross-sectional view taken along the line - in FIG. 49, and FIGS. 53 to 55 show the eleventh embodiment of the present invention. 53 is a plan view of the wiper arm, FIG. 54 is a cross-sectional side view thereof, and FIG. 55 is a plan view of the wiper arm.
20.40.720.740... wiper arm 41.
320.726.826.1026... Pivot shaft 50.750... Drive motor 6゛0.760... Leverage crank link (crank lever) 72.333.433.53.633... Operation lever - 92.193... Eccentric shaft 93.193.737.837.1037... Gear plate (ratchet gear) 99.743.843.1043... Motor (claw moving means) 100.742.842. 1042...Claw body 195.
...Motor (rotation drive means) 350...Auxiliary lever 360.460.560.580.660...Motor 361.461.561.581.661...Screw 370.470.570.590.670. ... Nut 550 ... Auxiliary lever 653 ... Cam groove 672 ... Pins 737a, 837a, 1037a ... Eccentric shaft portion (eccentric shaft) 1024 ... Lever of contact pressure changing mechanism 1037.10
72.1073... Gear (rotation transmission means) 1038... Cam plate (cam surface) 1071...
Swinging arm 1074... Eccentric shaft Fig. 30 Fig. 32 - Snake 672 Quantity of physical movement 100 Mw. Yo-King WJ"-' -〇〇Figure 40 Figure 41 Figure 44YIJ Figure 46 8X JIJ page 47

Claims (3)

[Claims] (1) A crank lever that is connected to the output shaft of the drive motor and rotates, and a swing lever that is connected to the pivot shaft of the wiper arm and swings are connected by at least one link arm, and one of these connection points , or the output shaft and the pivot shaft according to at least vehicle speed and wiper arm rotation position. (2) The one connection point is a connection point between the swing arm and the link arm, and the swing arm and link arm are connected by an eccentric shaft, and the movement drive means is rotated around the pivot shaft. A ratchet gear provided to be relatively rotatable with sliding resistance, a rotation transmitting means for transmitting the rotation of the ratchet gear to the eccentric shaft, and a claw body that meshes with the ratchet gear to stop its rotation. 2. The wiper device for a vehicle according to claim 1, further comprising a pawl moving means for moving the pawl between an engaged position and a disengaged position. (3) The one connection point is a connection point between the swing arm and the pivot shaft, and the movement drive means is provided as an eccentric that is relatively rotatable about the pivot shaft, and one end of the swing arm is connected to the drive means. a shaft, a ratchet gear integrally installed with the eccentric shaft so as to be able to rotate relative to the pivot shaft with sliding resistance; a pawl that engages with the ratchet gear to stop its rotation; and a pawl that engages with the ratchet gear to stop its rotation. Claim 1 further comprising a pawl body moving means for moving between an engaged position and a disengaged position.
The vehicle wiper device described.