JPS608561A - Crank gear - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] [Technical field of invention] The present invention relates to a crank gear.

This type of crank gear is used to drive the windshield wiper, which is moved beyond the normal wiping area and into a so-called sunken park position, which does not obstruct the view through said windshield. will be stopped.

[Technical background of the invention and its problems]

In known devices of this type, the eccentric is designed as a bushing, and the bushing is rotatably mounted on the crankpin.

A bushing rod is pivotally connected to the bushing, and the bushing rod drives the wiper like a pendulum through suitable means for transmitting movement. The effective crank radius can be varied by adjusting this eccentric bushing, and thereby the swiper angle can also be varied.

This known device has the disadvantage that the bushing rod can only be rotated in forward and reverse directions within a plane 1 perpendicular to the crank pin. However, it is clear in practice that due to manufacturing tolerances, this crank pin, the shaft driving the crank and the drive shaft supporting the wiper cannot be aligned exactly parallel to each other. In this known device, therefore, a tilting of the bushing opening, C, relative to the eccentric bushing must be avoided. This inclination increases friction loss and causes jamming of the drive mechanism.

In the known device, the torsionally rigid connection between the push rod and the eccentric push seat is achieved by direct engagement of a driver guided in a recess in the eccentric bushing with a recess in the bush rod. , achieved. For this reason, in the known device the bushing rod must be formed in a special shape and cannot be used without trouble with the usual bushing rods of other wiper devices.

[Purpose of the invention]

The object of the invention is to provide a crank gear that can operate without loss and is reliable even under complex installation conditions in a motor vehicle. As a result, the length of the crankshaft is not substantially longer than in known devices without the 74-way position of the hub, and the crank gear is made of components that can be easily manufactured. Can be assembled.

[Summary of the invention and its effects]

The above object of the invention is achieved by the invention as characterized by claim 1.

Due to the suspension of the bushing rod on the eccentric, sufficient mobility of this bushing rod is ensured in all directions, which allows the push rod to tilt during wiper operation. As a result, no friction losses occur at the movable shim. Here, even if the push rod is not precisely adjusted perpendicular to the bin, it can be adjusted perpendicularly to the rotational plane of the drive disk, thereby connecting the driver parallel to the υ axis. Positive engagement in the recess of the disc is ensured by a bushing rod which is connected in a twist-proof manner to a connecting disc which is rotatably mounted on the pin. Thereby, the coupling disc actually functions as an adjustment member that allows tilting and pivoting of the bushing rod relative to the beer pin.

Therefore, the essential feature of the invention is not only that the known eccentric bushing is constituted by an eccentric Dale pin. Rather, it is essentially a method of producing at the same time a torsionally rigid connection between this tiltable bushing rod and the eccentric with reliable operation. Compared to the known device mentioned at the outset, only one additional element is really necessary, and there is now the possibility of using a conventional push rod. This is because the recess for the driver is no longer provided in the push rod, but in the coupling disc.

A known crank gear eccentric is provided between the plate and the bushing rod. This plate is connected to the beer pin in a twist-proof manner, so that as simple as possible a torsion-proof connection is made between the eccentric and the push slot and between the eccentric and the bottle. are realized through axially parallel adjustable drivers, respectively. Also, this means that eccentricity d? Although achieved when a beer pin is used, the driver must be longer than an eccentric bushing due to the increased overall height of the beer pin. This requires great technical effort to make it possible to switch the driver from one shift position to another with little friction. Therefore, according to a particularly advantageous aspect of the invention, all components necessary for varying the crank radius are preferably arranged on the same side of the beer pin. Further, according to another embodiment characterized in claim (2), there is an effect on the installation. This is because the same member has only one or two eccentrics.
This is because even heavy pole pins can be used independently.

For a rigid connection to the screw between the bushing rod and the eccentric of the known device, in the direction of one revolution of the crank,
A pivotable spring-biased catch mounted on the bushing rod is additionally provided.
This catch is engaged in a recess in the generating surface of the eccentric.

A solution of this kind cannot be applied to the present invention without difficulty. This is because reliable engagement of this catch is not ensured when the push rod is tilted relative to the eccentric. According to an advantageous embodiment of the invention, it is therefore suggested that the catch is constituted by a spring-loaded slider adjusted radially relative to the beer pin. This slider is preferably
It is constructed in a sol socket that is fixed to the push rod. This is because the beer socket is injection molded from plastic material, so that the guide can be realized without great effort and without the need for additional parts.

[Embodiments of the invention]

Embodiments of the present invention will be described below with reference to the drawings.

The crank 10 is part of a crank gear.

This crank 10 is driven in a direction opposite to the direction of rotation by the drive shaft. Although the drive shaft is not shown in detail, it is inserted into the hole 11 of the crank 10. A pin 12 is fixed to the other end of the crank 10 in the form of a rivet, for example. A Dale pin 13 is movably attached to this pin 12. this? -The ball socket 14 is connected to the pin 13. Is this YJ? The pull socket 14 is fixed to a pull rod 15, only a portion of which is shown. The pin 13 is attached eccentrically to the pin 12, and this eccentricity is particularly apparent in FIG. There is an eccentric distance t'5 laterally from the central axis M of the pin 12 (there is an axis of symmetry S).Normally, the push rod 15 drives a windshield or one shaft via a rotating lever.This wiper shaft has a windshield A glass wire 9- is fixed.The wire angle 4- of this wire A?- is 13 with respect to the pin 12 as will be described later.
It depends on the position of.

Next, referring to FIGS. 1 and 5, the members necessary for performing the t7I replacement of the eccentric Dale pin 13 will be described. A connecting disk 20 is rotatably attached to the pin 12, and a dovetail projection 21 that projects vertically is formed on the connecting disk 2o. This dovetail protrusion 2) is formed integrally with the pole socket I4.
One protrudes between the side webs 22,23. As a result, the connecting disk 20td is connected to the bush rod 15 in a manner that prevents twisting, and due to its dovetail shape, the dovetail protrusion 21 is connected to the bush rod 15.
15 is prevented from tilting. As shown in FIG. 5, the connecting disk 20t/Ctri is further formed with a recess 24 having a circular cross section.

A driving disk 30 is rotatably attached to the pin 12 above the connecting disk 2o. As shown in FIG. 5d, this drive disk 3o has a recess 3 and an opening 32 formed at its periphery.

A plate 40 is fixed to the pin 12 above the drive disk 30 in a manner that prevents it from twisting. This plate 4θ is formed with a recess 41 opening at its periphery and a recess 42 spaced apart from the recess 41 in the circumferential direction.

The recess 24 of the coupling disk 20, the opening 32 of the drive disk 30 and the recess 41 of the plate 40 are formed such that the driver has a roll that can fit into each of these recesses.

A stud r51 is integrally provided on the Dale pin 13, and this stud 51 projects in parallel to the axial direction. The stud 5 is engaged with the recess 31 of the drive disk 30 in such a way that it is fitted from the side of the plate 40.

This prevents the drive disk 30 from twisting. −
It is connected to Lupine 13. If the roll 50 as a driver is the drive disk 3 as shown in FIG.
0 and into the recess 24 of the connecting disk 20, this allows the push rod 15 to be moved from the connecting disk 20 to the roll 50. Drive disk 30 and ? - a torsionally rigid connection of the pin 13 to the stud 5I is achieved; On the other hand, if the roll 50 is fitted into the opening 32 of the driving isk 3o as well as the recess 41 of the plate L/-) 40, the plate 40 will fit between the pin 12 and ball pin 13 fixed in a manner that prevents twisting. A rigid connection is achieved against torsion between the rolls 50 and 50.
The position of the crank 10 depends on the rotational direction of the crank 10 among other members.

A blind hole 52 opening toward the plate 4θ is eccentrically formed in the ball bottle 13.

A biasing pin 53 biased by a spring is guided within this blind hole 52. This biasing bottle 53
As shown in the figure, the minus side is inclined along the circumferential direction, and the plate 40 projects into a recess 42 located at a predetermined angular position with respect to the minus pin 13. Thereby, in the direction of one rotation of the crank 10, a torsionally strong connection between the ball pin 13 and the pin 12 through the grating 4° is also achieved through the biasing pin 53.
will be accomplished. Therefore, this biasing pin 53 also functions as a driver.

Furthermore, in one direction of rotation of the crank 1o, a strong connection against torsion can be achieved via the spring-loaded slider 54 between the bushing mouth, the door 15 and the male pin 13.

Is the slider 54 inside the guide 55? - It is attached movably in the radial direction of the pin 13.

As shown in detail in FIG. 1, the guide 55 is integrally formed within the goal socket 14. For the purpose of forming this guide 55, the goal socket 14 has a suitable stud 56 in the longitudinal direction of the bushing rod 15. The guide 55 is closed by a cover 57, and the cover 57 is fixed to the stud 56 by a shrink fit. In this case, the slider 54 is always aligned toward the center of the beer pin 13. This slider 64 cooperates with a stroke horn 458 on the generating surface of the beer pin 13, and this stroke horn 958 is adjacent to the driving slope 59.

FIG. 4 shows an embodiment of a member corresponding to the eccentric member shown in FIG. However, in this case, the eccentric member is 2
The double beer pin 60 is formed as a heavy beer pin 60, and another push rod 15' is connected to this double beer pin 60.

Furthermore, as is clear from FIG. 4, the plate 61
is arranged between the crank 10 and the coupling disc 20. A bellows seal 62 is provided between the plate 61 and the goal socket 14.

Furthermore, the embodiment of FIG. 4 differs from the embodiment of FIG. 1 in that the beer pin 60 occupies another switching position and the crank 10 occupies another angular position. The operation of such a rank gear will be explained below with reference to FIG.

FIG. 6a shows the crank gear in the position where the wiper, driven by the bushing rod 15, assumes its recessed four-way position.

Beer pin 13 is located in the position shown in FIG. 4 with respect to pin 12. The roll 50 is placed in the recess 4 of the plate 40.
2, thereby achieving a rigid connection with respect to the torsion between the pin 12 and the beer pin 13. If the crank now rotates counterclockwise, the relative position between ball pin 13 and pin 12 will be the sixth
As shown in Figure a, it is initially retained. As a result, the beer socket 14 is moved relative to the ball pin 13. During such a starting operation from the above-mentioned /4' position, the joint axis between the bushing rod 15 and the crank 10 thus becomes the axis of symmetry S of the guru socket 14.

FIG. 6b shows the position of the bushing rod 15 in the outer inverted position of the Waino motherboard. The sol 13 for the pi/12 is positioned at the position shown in FIG. In such an angular position, the stopper 58
As shown in FIG. 3, a slider 54 is in contact with the slider 54 . This allows for a connection between the push rod 15 and the push rod 15 that prevents twisting during counterclockwise rotation. -Lupine 1
It is brought between 3 and 3.

Furthermore, in such an angular position, the coupling disc 2
The 0 recess 24 is located exactly below the opening 32 of the drive disk 30 and the roll 50 acting as a driver is switched to engage the recess 24. This also results in a torsionally rigid connection between the bushing rod 15 and the beer pin 13 via this roll 50. After this, the unit consisting of the bushing rod and the sj-rupin is rotated by the rotation of the pin 12, as shown in FIG. 6b. Finally, the push rod 15 assumes the position shown in FIG. 6c, in which the wiper assumes its inwardly reversed position. This means a reversal position close to the park position. In this part of the operation, the joint axis between the push-button door 15 and the crank 10 corresponds to the center line M of the pin 12. If the direction of rotation of the crank does not change, the bushing rod 15 is
between the end positions shown in Figures b and 6c.

In addition, this adjustment lift has a magnitude of the horizontal angle α. During normal operation, the biasing pin 53 of the pole pin 13 is always fitted into the recess 42 of the plate 40 for a short time with the biasing force of the spring. However, the stop slope of the biasing pin 53 is
In the counterclockwise direction of rotation, plate 40 and pole pin 1
3 is adjusted in the circumferential direction so that a torsionally rigid connection between the two is not possible. Rather, the biasing pin 53 is repeatedly pushed back into the blind hole 52.

Now, if the direction of rotation of the crank 100 starting from the position of the bushing rod 15 in FIG. 6c is changed, it will initially remain in this state during normal wiper and operation. pin 1
The center line M of pin 12 functions as the joint axis between the push rod and the crank, and the generating surface of pin 12 functions as a support surface. As soon as the pussy lock P assumes the position shown in FIG. 6b, the biasing pin 53 engages in the recess 42 of the plate 40 and in this direction of rotation the biasing pin 53 engages the torsion between the tail pin 13 and the pin 12.

A solid connection is established. In this position of the push rod 15, the recess 4 of the plate 4o is positioned exactly above the opening 32 of the drive disk 30.

Now, if crank 10 is turned further, roll 5
0 is pushed up by the coupling disc 20 which is aligned with respect to the drive disc, thereby achieving a rigid connection with respect to the shaft and also to the torsion between the mail pin 13 and the pin 12.

As a result,? - the relative position between the tail pin 13 and the pin 12 no longer changes, so that the axis of symmetry S of the tail pin is again the joining axis;
The generated surface functions as a supporting surface. This brings the push rod back to the initial position of FIG. 6a, in which the wiper is stopped in the above-mentioned four-way position.

As is clear from Figure 6, during normal waist and arm movements,
The normal wiper angle, i.e. the adjustment lift of the bushing rod 15, is smaller than that during which the wiper reaches or leaves the park position. It is important to reach the same outward reversal position as shown, so that for this crank gear the wiper angle is enlarged only on one side.

[Brief explanation of drawings]

Figure 1 is a cross-sectional view of the crank gear, and Figure 2 is a cross-sectional view of the crank gear.
3 is a sectional view taken along line 111 in FIG. 1, FIG. 4 is a sectional view of a crank gear showing a modified example, and FIG.
The figure shows the constituent members, and FIG. 6 is a diagram for explaining the movement of the crank gear. 12...Pin, 13.60...Dale Pin, 14.
... Ball socket, 15.15'... Bush rod, 20... Connection disc, 24, 31, 41° 42
... recess, 30 ... drive disk, 32 ... opening, 40 ... plate, 51.58 ... stud, 5
2...Blind hole, 53...Biasing pin, 54...Slider, 55...Guide.

Claims (6)

[Claims] (1) A motor-driven crank having a pin, an eccentric attached to the pin, and a bushing rod connected to the eccentric; in a first direction of rotation of the crank, the eccentric The eccentric is connected in a twist-proof manner to the pin and in a second direction of rotation of the crank, the eccentric is connected in a twist-proof manner to the bushing rod via a driver that provides an adjustable form closure parallel to the axial direction. In the crank gear to be coupled, the eccentric is configured as a Dale pin (13), the bushing rod is provided with a Dale socket (J4) attached to this Dale pin, and the connecting disk (20)
is connected to the push rod in a manner that prevents twisting, and is rotatably attached to the pin (12). A crank gear is characterized in that it functions as an intermediate member of a rigid connection. (2) A driving disk (30) is rotatably attached to the pin (12) on the connecting disk (20), and a plate (40) is mounted on the driving disk (30) to connect the pin (12) to the connecting disk (20). 12), the ball pin (13) is arranged on the pin (12), and the driving disk (30) has an opening (32),
Connected to the Dale pin (13) to prevent twisting,
A driver (5σ) is guided in the opening (32) so as to be movable in the axial direction, and this driver is connected to the plate (4).
The crank gear according to claim 1, wherein the crank gear is engaged with either the recess (41) of the connecting disk (20) or the recess (24) of the connecting disk (20). (3) A stud (5)) protrudes from the Dale pin (13) parallel to the axial direction, and this stud (6)) is fitted into and engaged with the recess (31) of the drive disk (30). A crank gear according to claim (2), characterized in that: (4) A plate (40) is attached to the ball pin (13).
A blind hole (52) that opens toward One example is tilted and the plate (4
0) is engaged in a further recess (42) of the play) (40) of the goal bin (13) at a predetermined angular position relative to the goal bin (13). 3
) The crank gear according to any one of the items. (5) The eccentric is configured as a double Dale pin (60), and this beer pin (6θ) has two bush ports,
The crank gear according to any one of claims (1) to (4), characterized in that the wheels (xs, xs') are joined. (6) The bush rod (15) and the goal pin (1
3), a spring-loaded slider (54) is provided in the second direction of rotation of the crank (10), which slider is attached to the Dale socket).
(74) is installed in the id (55) so as to be movable in the radial direction of the Dale pin (13), and cooperates with the stud on the generating surface of the Dale pin (13). A crank gear according to any one of claims (1) to (5).