JPS6026740B2 - Windshield wiper device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a windshield wiper device that prevents a windshield wiper from lifting up when a vehicle is running at high speed.

The windshield wiper that wipes the front window glass of a vehicle is exposed to large wind pressure when the vehicle is running at high speed, and during the back and forth wiping operation, it may be lifted off the glass surface, especially during the return trip. This may result in poor wiping of the surface, which may significantly impede vehicle operation. This is because the speed of the wind hitting the wiper during the backward motion is the sum of the vehicle speed and the wiper interlocking speed. Reference is made to FIGS. 4, 5 and 6 to illustrate this in a commonly used wiper system.

In the general blade shown in Fig. 4, packing 8
holding claws 63, 63', 73a, 73a', 73b, 7
The distances between 3b' are all equal, and the loads P applied to each holding claw are also all equal. As shown in FIG. 4, this is symmetrical with the pin 51 as the center, so there are gaps between the pins 51 and 61, between the pins 61 and 51, and between the pin 71 and the holding claw 73a. distance is circle/2
, L/2, and L/2. The distributed pressing force per unit length of such a blade when the vehicle is stopped is as shown in FIG. 5, and the pressing force at both ends is extremely large. This means that the play rubber 9 shared by the holding claws 73a, 73a' at both ends is approximately 1.
This is because the length is only /2. In addition, the pressing force is large only at the holding claws, and it is 4.5 mm between the holding claws, but this is because the force applied to the packing 8 by the holding claws is only affected by the rigidity of the packing 8 between the holding claws. This is because power is distributed. When these blades are hit by high-speed airflow when traveling at high speed, the blades receive buoyancy and
The floating state at that time can be explained in FIG. In FIG. 6, the pressing force distribution of the conventional blade when there is no wind is shown by curve b, and the average value of the pressing force is shown by straight line Av, which is the value obtained by dividing the total pressing force by the total length of the plaid rubber 9. Similarly, when a high-speed airflow hits the plate, the buoyant force causes it to become curved as shown in curve b', and the sections Y, . It is shown that the play rubber 9 rises above the glass surface at Y2 and Y3. In particular, the central section Y2 is the area right in front of the driver, and if it were to rise even slightly in this section, it would significantly impede the driver's field of vision. As described above, even if the total pressing force is sufficient, the inappropriate pressing force distribution results in lifting at relatively low vehicle speeds, particularly in front of the driver. Therefore, various proposals have been made to prevent the wiper lifting phenomenon.

For example, one proposal is to strengthen the elastic force of the spring in the wiper device to make the pressing pressure of the blade rubber against the glass surface stronger than usual.

However, in this case, the contact friction between the blade rubber and the glass surface inevitably increases, so the motor that drives the wiper device not only needs to be powerful (large in size and consumes a lot of power). , causing chatter vibrations when the vehicle is running at low speeds, stopped, or while wiping away vibrations in drizzling rain.
This causes a problem that normal wiping is not performed. Also,
It is also known that a wing-like object is attached to the support metal fitting or support arm of the blade, and the force of the wind force hitting the wing-like object generates a force (reverse lifting force) that presses the blade rubber against the glass surface, thereby canceling out the lifting force.

In this case, it can be expected in principle that as the wind speed hitting the wing-shaped object increases, a corresponding blade pressing force will be generated. However, the wind direction and speed in front of the window glass are not uniform and simple, and there are many factors that cause the blades themselves to swing. However, depending on the distance from the vehicle and the direction of the wind, the wing-like object may be blown up by the wind and lifted off the glass surface, or it may cause chatter vibration. This may cause wiping failure. Also, gluing large wing-like objects may obstruct the vehicle operator's view, or
The reality is that the increased weight of the wiper causes structural and operational problems. The present invention has been made in view of the above points, and it is an object of the present invention to provide a windshield wiper device that has a simple configuration and is difficult to lift up during high-speed driving.

The present invention will be described below with reference to embodiments shown in the drawings.

In the wiper device shown in FIG.
, the head 2, and a link mechanism (not shown) connecting the two constitute driving means. As is well known, the rotational movement of the wiper motor is converted into rotational movement of the head 2 in the left and right directions by a link mechanism. With respect to this driving means, the arm 3 is connected to the head 2 at its rear end, and as the head 2 rotates, the arm 3 swings. A spring 4 is provided between the head 2 and the arm 3, and the arm 3 is loaded by the spring 4 toward one side using the connection portion with the head 2 as a fulcrum. This direction is the direction in which the play driver, which will be described later, comes into close contact with the glass surface, and the play driver is thereby pressed against the glass surface. Arm 3
A holding metal fitting is held at the tip of the holding metal fitting, and this holding metal fitting holds one arc-shaped primary lever 5, the same arc-shaped secondary levers 6, 6', and the same arc-shaped primary lever 5. It consists of yokes 7 and 7'. The central part of the primary lever 5 is rotatably attached to the tip of the arm 3 by a pin 51, and secondary levers 6, 6' are rotatably attached to both ends of the primary lever 5 by pins 61, 61. . Also,
The series of secondary levers 6 and 6' have pins 71 and 71.
The yokes 7, 7' are rotatably attached. At both ends of the two yokes 7, 7' and at one end of the secondary levers 6, 6', there are holding claws 72a, 72.
A packing 8 is attached by a', 72b, 72b', 62, and 62', and a play rubber 9 made of an elastic body is attached to the packing 8. These holding fittings swing the packing 8 and the play rubber 9 together with the swing motion of the arm 3, and the play rubber 9 is pressed against the glass surface by the spring 4, and in this state reciprocates on the glass surface and holds the glass. Wipe the surface.

The holding claws provided on the holding fittings in the windshield wiper device according to the present invention as described above are located between the first holding claws 72a, 72b and the second holding claws 72a', 72b' at both ends of the play rubber 9. L, the second holding claw 7
2a', 72b' and the third holding claws 62, 62', and if the distance between the third holding claws 62, 62' is -, then L>L2>L3. The force per unit length of the plate rubber 9 that is placed and further pressed against the glass surface is expressed as W, W2, W3, W4, and W5 in order from the holding claw 72b side in order to compare the forces between the holding claws. , W3>W2>W, and W3>W4>W5, and the distances between the holding claws L, L,
L, and the force P,, P caused by the spring 4 applied to each holding claw considering the rebound force caused by the packing 8, which will be described later.
2. Position each pin A, B to determine P3.
・,E can be determined.

Here, when the above-mentioned W,, W2, . . . W5 are expressed as an equation, it becomes as follows. In addition, f. , f2・”...f6 represents the rebuttal force of packing 8. Next, P,, P2, P3 and L,
f2...f6 will be explained in detail.

The relationship between the distances A, B, . . . E between P,, P2, P3 and the positions of the pins as shown in FIG. W: Total load given by spring 4, W6,: Load on pin 61, W7,: Pin 71
If the load is W6. = Appearance = Shout 10 P Rei A p3 = W61 x Plasterer B = p, 10 P2, w7, = W61 x Medium Re PI Ni W71 X Poison 3 C P2 = W71 The relationship between the distances L, L, L3 between the holding claws and the distances A, B, ...E between the pin positions is L=C+D
, shi=A+B−D, Li2×(E−B).

In addition, as shown in FIG. 3, in order to completely align the play rubber 9 with respect to an arbitrary glass curved surface, the force required to bend the packing 8 and the play rubber 9 is f at each holding claw position starting from the end. ',, f'2, . . . r6.

Here, f',, f'2, """f'6 are based on the plane passing through the holding claws 72a' and 72b' of the packing 8,
This can be considered as a problem of an unsteady beam with the positions of the holding claws 72a' and 72b' as fulcrums. Therefore, the distances from the reference surface to the glass curved surface at other holding claws excluding the fulcrum position were set to 6. , 63, 64, and 66, and the bending rigidity of the packing 8 is EBIB, and the plate rubber 9 is
If the bending stiffness of is ERIR, then the bending stiffness EI of the packing 8 and plaid rubber 9 is E1-EB18.
1ERIR, but since EB》ER is well known, E1=EBI
It becomes B.

Therefore, in consideration of the above points and the fact that the beam is uncertain, the relationship between the holding claws 72b and 72b' will be explained in detail.

In FIG. 3, if the distance from the holding claw 72b on the side closer to the head 2 is x, then the amount of deflection y is expressed as y=odd+CIX+C2 according to a known formula.

However, C,, C2 are integral constants. Similarly, the formula for the amount of deflection between each holding claw (y2, y3, y4, y5
) is determined, and each integral constant is determined based on each boundary condition, then the amount of deflection y. ,y2,.・・・-．・y5 is y,=h, (f',, f'3, f'4, f'6EI)
,y2=h2(f',,f'3,f'4,f'6,EI
), y3=h3(f',, f'2, f'4, f'6, E
I), y4=L(f',, f'2, f'4, f'6, E
I), y5=mu(f',, f'2, f'4, f'6, E
I).

However, h,, h2, . . . h5 represent functions. Here, the amount of deflection at each holding claw position is as shown in Figure 3.
6,, (6230), 63, 64, (6530), 66
Therefore, according to the above deflection formula, y,
x=0=8,=h,(f',, f'3, f'4, f'6
, EI) y Matsuni.

D63 Nih3 (f'1, f'3・r4・f'6・EI
) Y-board! 0264 nih4(r1, r3・f'4・r6
・EI) Y string D.

D66 Nih5 (f'1, f'3・f'4・r6・EI
), and the four unknowns (f',, f'3, f'4, f
'6), a simultaneous equation of four equations is established.

Also, since the left and right rotation moments of the packing 8 are equal, f'2 and f'5 are f'.・(4,1220 L3
) 10f'3 ・(L10L2) 10f'4 ・(LI10L20-)=r2・
L, 10f'5 (L, 1220L3), from the balance of vertical forces, f'20f'5=f', 10f'30f'4
The formula 10f'6 is established, and f'2=h8(f',, f
'3, f'4, f'6) f'5=h7(f',, f'3
, f'4, f'6) are obtained.

However, h6 and h7 represent functions. From the above four simultaneous equations and the formula ``2, f'5, f',, f'2
......, finding f'6, f',=g, (6,,6
3, 84, 66, EI) f'2 = g2 (6,, 63, 6
4, 66, EI) f'3 = g3 (6,, 63, 64
, 66 , EI) f'4 = g4 (6, , 63, 64, 6
6, EI) f'5 = g5 (6, 63, 64 , 66,
EI) f'6; g6 (6,, 63, 64, 66, EI)
becomes. However, g,, g2, . . . g6 represent functions. In addition, EI is determined by the shape and material of the packing 8, and 6. , 63, 64, 66 can be determined from the shape of the glass surface, and as a result f',, f'2,...
The force necessary to bend the packing 8 and plaid rubber 9 of r6 is obtained. Here, f',, f'2, . . . r5 can be determined assuming that the direction of the arrow in FIG.
=-f'2, ra=r3, f4=r4, 乍=-r5, f6=r6, It is obtained as follows.

As shown in Fig. 2, as shown in Fig. 2, the above has the effect of preventing a decrease in the pressing force between the holding pawls and making the pressing force at the center of the blade rubber higher than the average, thereby improving the blade lifting prevention performance. Obtainable.

In fact, the distribution of the pressing force of the Wiper device of the present invention, which is shown in FIG. The average value is shown by the straight line Av.

In addition, when a high-speed airflow hits the blade when the vehicle is running at high speed, the pressing force of the blade rubber 9 becomes as shown by curve a', and the raised portion becomes the blade sections X, X2, and the raised portion of the conventional wiper device. Compared to the portions Y, Y2, and Y3, only the end portions are in a raised state, and in particular, only a portion of the portions Y, Y3 in front of the driver is raised, so that the visual field is less obstructed. In addition, in the above embodiment, L on the right side and L on the left side
However, this may be slightly different, and there is no need to be symmetrical about the pin 51. In short, the central part of the blade is supported densely, and the blades are supported loosely toward both ends, and the pressing force is small. What we need to do is to make the distribution stronger as it goes toward the center.

As described above, in the device of the present invention, when the same high-speed airflow hits the playing day as the above-mentioned high-speed airflow, the pressing force distribution becomes like the curve a' shown in FIG. In a, the blade rubber 9 is floating above the glass surface, but it is not as big an obstacle as it is in the center, and the pressing force distribution is relatively smooth, so the area where it lifts up is also smaller than that of a regular blade. is decreasing.

Therefore, in the device of the present invention, when the lifter tries to lift up when the vehicle is running at high speed, a large part including the area in front of the driver does not lift up, but even in the worst case, the area in front of the driver is secured. It is possible.

Furthermore, in order to adapt to current vehicles having windshields with curved surfaces with different curvatures depending on the wiper wiping position and vehicle type, especially for passengers, the present invention provides a repulsive force of the packing and play rubber corresponding to the curvature of the curved surface. This has the excellent effect of being able to obtain the optimum class pressure distribution for each vehicle type.

[Brief explanation of drawings]

FIG. 1 is a front view of a wiper device which is an embodiment of the present invention;
Fig. 2 corresponds to the embodiment shown in Fig. 1 and is a diagram showing the distribution of pressure force per unit length of the play driver pressed against the glass surface when the vehicle is stopped; Fig. 3 corresponds to the embodiment described above. Figure 4 shows the front view of the conventional Wipper device; Figure 5 shows the pressing force per unit length of the blade of the conventional device when the vehicle is stopped. Diagram showing the distribution: and the sixth
The figure is a pressing force distribution diagram per unit length of an embodiment of the present invention and a conventional example, showing the floating state when the blade receives buoyancy due to high-speed airflow during high-speed running. 1...Wiper motor, 2...Head, 3...Arm, 4
...Spring, 5, 6, 6', 7, 7'...
Holding metal fitting, 5...Primary lever, 51, 6
1,71...Pin, 6,6'...Secondary lever, 6
2,62'...Retaining claw, 7,7'...
Yoke, 72a, 72, 72b, 72U...holding claw,
8... Packing, 9... Play rubber. Figure 6 Ship chart N Ship chart dimensions Rudder diagram vertical

Claims (1)

[Claims] 1. A blade rubber made of an elastic body, a backing for holding the blade rubber, a holding fitting for holding the bucking, an arm for holding the holding fitting, and a blade rubber for pressing the blade rubber against the glass surface of the vehicle. A six-point device comprising a spring that loads the arm, and a driving means that is connected to the arm and swings the arm, the holding fitting, the buckling, and the blade rubber, and having six holding claws of the holding fitting. a supporting wiper blade, the first retaining pawl to the second retaining pawl at both ends of the blade;
The distance L_1 to the holding claw position is made larger than the distance L_2 from the second holding claw to the third holding claw, and further the distance L_3 between the third holding claws near the center of the blade. When the blade rubber is pressed against the glass surface with the blade in close contact with the glass surface having a certain curvature with The value obtained by subtracting the repulsive force between the bucking and the blade rubber from the force directed toward the blade is calculated as the distance L between each of the holding claws.
The force W_1, W_2, W per unit length between each of the holding claws corresponds to the value divided by _1, L_2, L_3.
_3, W_4, W_5 are such that the force per unit length W_3 between the holding claws at the center of the blade is larger than the forces per unit length W_2 and W_4 on both sides thereof, and the unit length at both ends of the blade A wind seal wiper device characterized in that each of the holding claw positions and the holding fitting mounting position are determined so that the force per unit length W_1, W_5 is smaller than the adjacent force per unit length W_2, W_4. .