GB1566452A

GB1566452A - Rearview mirror with setting or adjusting means

Info

Publication number: GB1566452A
Application number: GB1841879A
Authority: GB
Original assignee: Individual
Current assignee: Individual
Priority date: 1975-09-30
Filing date: 1976-09-24
Publication date: 1980-04-30

Description

(54) REARVIEW MIRROR WITH SETTING OR ADJUSTING MEANS (71) I, ERICH WUNSCH, a German national, of 12 Im Hofrain, Schwieberdingen, Germany, do hereby declare the invention, for which I pray that a patent may be granted to me, and the method by which it is to be performed, to be particularly described in and by the following statement:- The invention relates to a rearview mirror with setting or adjusting means for motor vehicles or the like with the aid of which the rearward field of view of the drivers can be adapted also when the vehicle is travelling both to his sitting and driving position and to the particular traffic situation.

To solve this problem a great variety of special forms of rearview mirrors has already been proposed but none of them has so far been complete satisfactory. Thus, a rearview mirror is known which has two mirror plates in which in addition to the normal mirror plate, which covers the rearward road area, a second mirror plate is provided which is angled with respect to the first along a substantially vertical line and covers an area lying more to the side of the vehicle so that with this mirror assembly a total of two images results. These two images frequently irritate the driver because simultaneous consideration and correct interpretation of the two images requires special concentration and in particular practice. Experience has shown that many users of such divided mirrors require a long familiarisation time before they can use them properly and in some cases never become able to do so. Moreover, the blind angle is still not completely eliminated because motor or pedestrian traffic for example directly adjacent a vehicle is still not visible and this is a frequent cause of serious accidents.

The problem underlying the present invention is therefore to construct a rearview mirror so that it provides adequate viewability not only of the rearward road area but also, preferably simultaneously, of the lateral area adjacent the vehicle up to the level of the driver and of the area beneath the lateral field of view and thus substantially eliminates a blind angle.

According to the invention, there is provided a rearview mirror for a vehicle or the like, the mirror having a housing; a mirror plate; a first joint connecting the mirror to the housing, said joint being spaced from the centre of the mirror towards one edge thereof, said joint providing for tilting of the mirror about two axes perpendicular to each other, first tilting means located adjacent said edge for tilting the plate about the first of said axes, second tilting means located adjacent said edge for tilting said plate about the second of said axes, actuating means for moving said second tilting means including a second joint having relatively slidable members which move relatively to each other to permit tilting of the plate about the first axis and which connect with each other to actuate said second tilting means, electrical motor means for actuating the first tilting means and for actuating the second tilting means via the second joint; and means for mounting the housing on a vehicle bodywork so that the first axis is substantially vertical and the second axis is substantially horizontal.

The or each electric motor may, for example, be controlled by the flasher for the direction indicator of the vehicle so that the mirror plate adjustment into the laterally and vertically tilted position takes place whenever the flasher is operated for an overtaking manoeuvre.

The mirror pivoting may be effected in time with the flasher or via an additional switch which is actuated for a brief time when the flasher is switched on.

Stops may be provided for the mirror plate which permit an individual setting of the lateral and/or vertical tilt angle adapted to the particular driver position independently of the adjustability of the mirror housing generally provided.

A further individual adjustability of the lateral and vertical tilt angle is provided by the arrangement of a control disk in the control slot of which the pin carrying the mirror plate is guided and limited in its angular deflection by adjustable stops.

The electrical power supply of the or each electric motor is connected to the vehicle electrical system in such a manner that when the vehicle ignition is switched off the mirror plate pivots automatically into the lateral and/ or vertical position so that the driver can see the lateral area of the vehicle in the rearview mirror before opening the vehicle door.

To eliminate misinterpretation of the image apparent to the driver in the rearview mirror it may be advantageous to provide a switch which controls a control indication in the interior of the vehicle which indicates by an optical and/or acoustic signal to the driver in which pivot position the mirror plate is disposed.

Rearview mirrors for vehicles and the like, having setting or adjusting means are also the subject of British Patent Specification No. 1 566 451 (Application 39701/76) from which this specification is divided.

The invention will be explained in detail hereafter with the aid of the examples of embodiment illustrated in the drawings, wherein: FIGURE 1 is a schematic plan view of a road with two vehicles, FIGURE 2 is a schematic side elevation of the left side of a vehicle and a cyclist, FIGURE 3 is a schematic partially hori zontally sectioned plan view of the essential parts of a mirror according to a first example of embodiment, FIGURE 4 is a rear view in the direction of the arrow XVII of Figure 3, FIGURE 5 is a detail, seen in the direction and height of the arrow XIX of Figure 3, FIGURE 6 is a detail seen in the direction and height of the arrow adjacent the motor 251 of Figure 3, FIGURE 7 is a schematic perspective rear view of the essential parts of a mirror accord ing to a second example of embodiment, FIGURE 8 is a rear view corresponding substantially to Figure 4 according to a third example of embodiment, FIGURE 9 is a plan view of the parts in Figure 8, FIGURE 10 is an axial partially sectioned end elevation of a return stop of a fourth example of embodiment, FIGURE 11 is a vertically sectioned rear view of a mirror according to a fifth example of embodiment, FIGURE 12 is a schematic partially horizontally sectioned plan view of the mirror of Figure 1.1, FIGURE 13 is a schematic end view of the right adjusting means in the direction of the arrow XXVII of Figure 11, FIGURE 14 is a schematic end view of the left adjusting means in the direction of the arrow XXVIII of Figure 11, and FIGURE 15 is a schematic plan view of the mirror plate in two positions.

Figure 1 shows a road 10 with normal lane 11 and overtaking lane 12 on which a vehicle 13 is being overtaken by a vehicle 14. The exterior rearview mirror 15 of the vehicle 13 is constructed according to the invention. In the rest position of the mirror 15 the driver of the vehicle 13 has the angle of view 16.

The vehicle 14 is not visible in the mirror 15 of the vehicle 13. The angle 17 of view shown in dashed line results for the driver of the vehicle 13 when the mirror 15 has been adjusted out of the rest position about a substantially vertical axis to the left outwardly into a laterally tilted position. The vehicle 14 is then in the field of view of the driver and not in the blind angle.

Figure 2 shows alongside the vehicle 13, but beneath the lateral angle of view of the driver, a cyclist with bicycle 18. In the rest position of the mirror 15 the vertical angle of view 19 is obtained. The bicycle 18 is not visible for the driver of the vehicle 13. The mirror 15 obviates this blind angle as well.

The vertical angle of view 20 results when the mirror is moved out of its rest position about a substantially horizontal axis downwardly into a vertically tilted position. The bicycle 18 is then visible in the mirror 15.

Thus, a blind angle may be eliminated by means of the mirror both in the lateral direction and in the vertical direction.

In the embodiment shown in Figures 3 to 6 of a mirror the mirror plate 211 is moveably disposed in the mirror housing 212. By means of a remote-controllable adjusting means 213 the mirror plate 211 is pivotal by tilting against the action of a cylindrical coil spring 228 about the spatially substantially vertical axis 215 and/or horizontal axis 216. This is made possible by a ball joint having a ball 217 fixed on the housing 212 and a ball socket 218 mounted on the back of the mirror plate 211. The joint 217, 218 is spaced from the centre of the plate 211 towards one edge thereof. The mounting is also effected by means of a two-axis joint whose centre is disposed in the continuation of the axis 216 spaced from the ball 217. The two-axis joint comprises a bearing head 219 which is mounted pivotally on the housing 212 about an axis 220 parallel to the horizontal axis 216 and comprises a guide slot 221 which extends substantially perpendicularly to the bearing axis 220. Also part of the two-axis joint is a cylindrical guide pin 222 which extends substantially perpendicularly to the mirror plate plane and is secured to the back of the mirror plate 211. The guide pin 222 passes through the guide slot 221 practically without play in the direction of the slot and transversely thereof so that when the mirror plate pivots in the ball joint 217 or 218 about the axis 215 (arrow 223 Fig. 6) a relative displacement occurs between the guide pin 222 and the guide slot 221 substantially in the longitudinal direction of the pin whereas when the mirror plate tilts about the axis 216 (arrow 224 Fig.

5) a positive coupling obtained between the guide slot 221 and guide pin 222 and a tilting movement about the axis 216 and the bearing axis 220 is thus effected, for example via a tab-like lever arm 225 which is connected to the bearing head 219.

The coil spring 228 engages with one end 229 (Figure 4) on the mirror plate 211 and is held with its other end 230 on the housing 212.

The adjusting means 213 comprises a first electrical gear motor 251 for the pivoting of the mirror plate 211 in the arrow direction 223 about the axis 215 and a second synchronized gear motor 252 for the tilting adjustment in the arrow direction 224 about the axis 216, these motors being mounted on the housing 212.

Mounted on the output shaft of the first gear motor 251 is an eccentric cam disk 253 as pivoting adjusting element. Mounted on the output shaft of the second gear motor 252 is an eccentric cam disk 254 as tilting adjusting element. The latter bears with the peripheral face on the side of the tab 225 remote from the mirror plate 211. The first cam disk 253 lies with its peripheral face for example directly on the back of the mirror plate 211 spaced from the ball joint 217, 218.

The tilting means 253 and 222, 219, 254 are also located adjacent said edge of the mirror plate 211.

The electrical supply lines and control lines of the gear motors 252, 253 are arranged in the housing 212 and for example lead to a compound slide switch in the interior of the vehicle via which the connection and control of the gear motors 251, 252 can be effected in the desired manner.

In Figures 3 and 5 the second cam disk 254 is shown in a rotary position of maximum eccentricity (Figure 5).

If by switching on the gear motor 252 the cam disk 254 is turned further out of the maximum eccentric position the mirror plate 211 is caused to follow via the spring 228 because the tab 225 is pressed via said spring against the cam disk 254. On minimum eccentricity of the cam disk 254 the tab 225 pivots to the left in Figure 5. Via the coupling between the tab 225, bearing head 219 with guide slot 221 and guide pin 222 the mirror plate 211 is also correspondingly inclined (dashed line in Figure 5).

Regarding the pivot position of the mirror plate 211 about the axis 215, Figure 3 shows an end inward position. The cam disk 253 is in a position of minimum eccentricity. If the gear motor 251 is switched on and the cam disk 253 turned from this position into the maximum eccentricity position the cam disk 253 presses onto the back of the mirror plate 211 and pivots it about the vertical axis 215 (arrow direction 223). The guide pin 222 then moves within the guide slot 221.

In the second embodiment (Figure 7), in contrast to the first embodiment, a single electric motor 233 is provided for the tilting adjustment (arrow 224) and the pivoting adjustment (arrow 223), the movements in the two directions of rotation 223 and 224 being brought about by changing the direction of rotation of the electric motor. The takeoff of the gear motor 233 is via the output shaft 240 thereof to two coaxial eccentric cam disks 238, 239 via two oppositely installed freewheels 247, 248 clamped to the output shaft 240. These two cam disks 238 and 239 move the mirror plate 211 via the associated tab 225 or directly via the eccentric cam 253 in the two directions of rotation according to the arrows 223 and 224.

The third embodiment (Figures 8, 9) corresponds as regards the adjusting means to the second example of embodiment with only one gear motor and two coaxial cam disks driven thereby. There is a kinematic reversal compared with the second example of embodiment so that in Figures 8, 9 the bearing head 319 is mounted on the mirror plate 311 for pivotal movement about the bearing axis 320, through an angle piece 355 which is secured with one leg on the mirror plate 311 and accommodates in the other leg the bearing head 319 for pivotal movement about the bearing axis 320. The perpendicularly bracing clamp 325 is mounted on the angle 355. The guide pin 322 is secured to the mirror plate holder 312 instead of to the mirror plate.

In Figure 10 as fourth embodiment a return stop 280 is shown which can be provided for each cam disk 238, 239. The return stop 280 is in the form of a friction brake with a stationary friction element 289 which is mounted for radial displacement in a stationary holder 284 and is pressed by means of a spring 290 adjustably arranged in the holder 284 and effective in the radial direction with its friction face 291 permanently on a peripheral portion of the stop disk 281. In another embodiment which is not illustrated the friction element 289 is not pressed against the stop disk 281 but against a peripheral portion of the cam disk itself or of the shaft sectior non-rotatably secured thereto. In another em bodiment a brake disc which presses on the end face of the cam is used instead of a brake block as friction element.

The fifth embodiment (Figures 11-15) corresponds fundamentally to the first embodiment (Figures 3 to 6) the description of which applies essentially to the fifth embodiment as well.

The bearing head 419 is pivotally mounted in the holder 413 fixed with respect to the housing. The guide slot 421 is open to the right. The mirror plate pivoting in the ball joint 417, 418 about the axis 415 leads to a pivoting in the direction of the arrows a and b (Figure 15) and a mirror plate tilting about the axis 416 to a movement in the direction of the arrows a and b in Figure 13. For the adjustment two electrical reversible directcurrent gear motors 430, 431 are provided each having driven eccentric disks 440 and 441 respectively, the first gear motor 430 with the eccentric disk 440 serving for pivotal adjustment of the mirror plate 411 about the vertical axis 415 and engaging the mirror plate 411 via a U-shaped fork 450, whereas the second gear motor 431 with the eccentric disk 441 serves for the tilting adjustment about the axis 416 and engages by means of a U-shaped fork 451 on the bearing head 419.

For switching on the gear motor 430, 431 a switch is provided on the vehicle dashboard which like a crane switch in logical manner switches the gear motor 430 and/or 431 on corresponding to the desired pivot or tilt position. The two fork legs 452, 453 of the first fork 450 and in similar manner the two fork legs 454, 455 of the second fork 451 engage over the associated eccentric disk 440 and 441 respectively within the disk plane and substantially free of play and not spaced from the outer peripheral face 442 and 443 respectively. There is only point contact. On revolution of the first eccentric disk 440 in the right direction (arrow a shown in full line) the right fork leg453 in Figure 14 is subjected to the action of the peripheral face 442 of the eccentric disk 440 whereas the opposite fork leg 452 is only in point contact with the peripheral face 442 in substantially play-free manner. When the second eccentric disk 441 revolves in the left direction of rotation (Figure 13, arrow a) the fork leg 455 is acted upon by the peripheral face 443 of the eccentric disk 441 whilst the opposite fork leg 454 is only in point contact with said peripheral face 443 in substantially play-free manner.

The left fork 450 in Figures 11, 12 is pivotally mounted with respect to the housing 412 about an axis which can extend substantially parallel to the two fork legs 452, 453 and to the axis 415. The first eccentric disk 440 is, seen transversely of the disk plane, in the form of a spherical section so that the outer peripheral face 442 thereof has the form of a circular arc. The fork 450 is operatively coupled to a pivot lever 460 which engages the frame 410 by means of a pull-push mounting but is otherwise freely moveable. The operative coupling in the power path between the fork 450 and the pivot lever 460 and in the power path between the second fork 451 and the bearing head 419 is in each case a slip clutch with adjustable slip behaviour. For this purpose the pivot lever 460 and the first fork 450 are arranged on a pivot sleeve 461 and clamped together with interposition of the slip clutch. Similarly, the bearing head 419 and the fork 451 are disposed on a common head shaft 462 and tensioned together with interposition of a slip clutch. The slip behaviour of each slip clutch is adjustable via the axial tensioning force in such a manner that the torque necessary to overcome the static friction of the slip clutch is greater than the drive torque necessary for the pivot drive or tilt drive of the mirror plate 411 about the axis 415 or 416 respectively.

The bearing head 419 is non-rotatably mounted on the head shaft 462 which carries a non-rotatably mounted coupling disc 463 and a slip or brake-lining disk 465. The fork 451 is traversed by the head shaft 462 in spaced relationship substantially at right angles to the fork legs 454, 455 thereof and by means of an adjusting nut 466 with interposed spring washers 467 held on the head shaft 462 and pressed with adjustable spring force against the lining disk 465 and the clutch disk 463.

Thus, the mirror plate 411 may be tilted manually about the axis 416 with the eccentric disk 441 and fork 451 stationary by pivoting the bearing head 419 with head shaft 462 and coupling disk 463, overcoming the static friction of the lining disk 465, relatively to the fork 451 about the bearing axis 420. The mirror plate 411 can be manually adjusted in this manner with the drive stationary.

The pivot lever 460 and the fork 450 are mounted spaced from the fork legs 452, 453 pivotally on the pivot sleeve 461 which is pivotally moveable on a journal 424. Disposed on the pivot sleeve 461 between the pivot lever 460 and the first fork 450 is a slip or brake lining disk 470. The fork 450 is adapted to be pressed by means of an adjusting nut 471 screwed onto the pivot sleeve 461 with interposed spring washers 472 with adjustable spring force against the lining disk 470 and the pivot lever 460 so that the mirror plate 411 when the eccentric disk 440 and fork 450 are stationary is pivotal manually about the axis 415 by pivoting the lever 460, overcoming the static friction of the lining disk 470, relatively to the fork 450 about the axis of the pivot sleeve 461. When the gear motor 430 is stationary the mirror plate 411 can thus be pivoted manually also about the axis 415.

The pull-push mounting of the pivot lever 460 comprises a ball 480 at the pivot lever end and said ball bears on the back of the frame 410 of the mirror plate 411. Furthermore, a substantially angular flat spring 481 is mounted on the back of the frame 410. The ball 480 is accommodated between the angle leg 482 of the flat spring 481 and the back of the frame 410, the lever 460 thus exerting a pull-push effect on the mirror plate 411 but otherwise being freely moveable.

Each eccentric disk 440, 441 with fork 450 and 451 respectively comprises an end stop means for disengaging the gear to limit the revolution movement of the eccentric disk 440 and 441 in the two drive direction of rotation (arrows a, b) to a peripheral angle of about 1800 and separate the eccentric disks 440 or 441 from the drive. For disengaging the gear a slip clutch is disposed between each of the eccentric disks 440, 441 and its drive member and the slip behaviour of said clutch may be adjusted via the axial tensioning force so that the torque necessary to overcome the static friction of the slip clutch is greater than the drive torque necessary for the pivot drive (axis 415) or tilt drive (axis 416) of the mirror plate 411 about the axes 415 and 416.

The first eccentric disk 440 is rotatably mounted on a bush 444 fitted on the motor 430 on a stationary journale 426, a drive gear 446 also being arranged on said bush and meshing with the driven pinion 445. Between the drive gear 446 and eccentric disk 440 on the bush 444 there is a slip or brake lining disk 447 which is adhered to the drive gear 446 or the eccentric disk 440. The eccentric disk 440 is adapted to be pressed by means of an adjusting nut 448 screwed onto the bush 444 with interposed spring washers 449 with adjustable spring force against the lining disk 447 and the drive gear 446 so that when the eccentric disk 440 runs against one of the end stop means and is held fixed said disk may be uncoupled, overcoming the static friction of the lining disk 447, by the drive gear 446, the latter continuing to rotate with reduced speed.

The eccentric disk 441 is correspondingly rotatably mounted on a bush 432 mounted rotatably on the associated gear motor 431 on a journal 427 and on this bush a drive gear 434 meshing with the driven pinion 433 of the gear motor 431 is also mounted. Arranged on the bush 432 between the drive gear 434 and second eccentric disk 441 is a slip or brake lining disk 435 which is adhered to one of these two. The eccentric disk 441 is pressed by means of an adjusting nut 436 screwed onto the bush 432 with interposed spring washers 437 with adjustable spring force against the lining disk 435 and the drive gear 434.

Each eccentric disk 440, 441 comprises on the end face remote from the gear motor 430 or 431 respectively an axially projecting stop pin or tab 484 and 485 respectively. The second fork 451 carries on the inside of each fork leg 454, 455 a blocking pin 486 or 487 substantially perpendicular thereto which with its free end projects into the path over which the stop pin 485 travels radially up to the eccentric disk centre and when the disk 441 is pivoted in both directions of rotation (arrows a and b) through in each case about 1800 peripheral angle forms an end stop for the stop pin. The eccentric disk 441 can thus rotate in both directions according to the arrows a and b only through about 1800 peripheral angle in each case. Alternatively, the end stop means may be adapted to the eccentric disk 440. The eccentric disk 440 may have associated therewith two stud bolts 488 and 489 fixed with respect to the housing.

The stud bolts 488 and 489 lie on the track through which the stop pin 484 travels when the eccentric disk 440 is pivoted in both directions of rotation according to the arrows a and b through in each case about 1800 peripheral angle. The two stud bolts 488 and 489 form with their free upwardly directed end face the end stop for the stop pin 484.

If the mirror plate 411 is to be pivoted about the axis 415, for example, in the direction of the arrow a (Figure 15), the gear motor 430 is switched on by correspondingly actuating the switch. The eccentric disk 450 is thus driven via the driven pinion 445, the drive gear 446 and the lining disk 447 in the right direction according to the arrow a in Figure 14. The eccentric disk 440 rotates with increasing eccentricity and acts with its peripheral face 442 on the fork leg 453. The fork 450 and, coupled thereto via the lining disk 470, the pivot lever 460 are thereby pivoted about the axis of the pivot sleeve 461 in the direction of the arrow a. The ball 480 thus presses against the back of the mirror plate 411 also in the pivot direction a. When the eccentric disk 440 has reached the end position shown in Figure 14 the stop pin 484 meets the stud bolt 489 and blocks the pivoting. The gear motor 430 then continues to run with reduced speed, since the gear 446 is further driven via the driven pinion 445, the static friction due to the lining disk 447 being overcome so that when the eccentric disk 440 is stationary the drive gear 446 can continue to rotate.

If the mirror plate 411 is to be pivoted in the opposite direction (arrow a) about the axis 415, the switch is correspondingly actuated so that the gear motor 430 drives ths eccentric disk 440 in the opposite sense (arrow b, Figure 14). The fork 450 with the pivot lever 460 pivots about the axis of the pivot sleeve 461 in the opposite direction (arrow b), the mirror plate 411 thus being pivoted into the position shown in dashed lines in Figure 29.

If the adjusting facility via the gear motor 430 has failed, the mirror plate 411 can be manually pivoted into both positions (Figure 15). For pivoting the mirror plate 411 in the arrow direction b (Figure 15) a pressure is exerted on the mirror plate 411 at the mirror edge opposite the ball 417. The mirror plate presses via the ball 480 onto the pivot lever 460 and attempts to pivot the latter about the axis of the pivot sleeve 461. Since when the gear motor 430 is stationary, due to the selflocking of the gear, the eccentric disk 440 is also non-rotatable, on this pivoting of the lever 460 the fork 450 cannot be entrained.

However, the pivot lever 460 can pivot relatively to the fork 450 about the axis of the pivot sleeve 461 and change its relative angular position with respect to the fork 450 in that the static friction between the lever 460 and fork 450 is overcome, which is due to the lining disk 470. The pivot lever 460 thus slips in the region of the disk 470 with respect to the fork 450 about the axis of the pivot sleeve 461. When the gear motor 430 is again ready for operation, the mirror plate 411 is pressed manually against a rear stop 94 (Figure 15) fixed with respect to the housing and the gear motor 430 switched on by corresponding actuation of the switch so that it brings the eccentric disk 440 out of the one end position (Figure 14) by rotation in the arrow direction b into the other end position. At the latest on reaching this other end position the pivot lever 460 and the fork 450 have again reached the relative rotational position with respect to each other which they had before manual adjustment of the mirror plate 411. By corresponding switching of the switch the eccentric disk 440 is now driven in the arrow direction a so that the mirror plate 411 is pivoted by the motor in the arrow direction a or oppositely in the arrow direction b (Figure 15).

The tilting adjustment of the mirror plate 411 about the axis 416 is effected in similar manner. For this purpose, the switch is correspondingly actuated, for example so that a mirror adjustment takes place in the arrow direction a (Figure 13). The eccentric disk 441 is driven in the arrow direction a and the fork leg 455 acted upon by the eccentric disk 441. The fork 451 is pivoted in the arrow direction a about the axis 420, which effects a pivoting of the bearing head 419 with guide pin 422 and thus of the mirror plate 411. The pivotal movement of the eccentric disk 441 is terminated when the stop pin 485 meets the blocking pin 487. The eccentric disk 441 is then stationary but the gear motor 431 continues to run, with reduced speed. The drive gear 434 is further driven, the static friction of the lining disk 435 being overcome, If the mirror plate 411 is to be adjusted by the electric motor in the opposite direction (dashed line in Figure 15) the switch is brought into the corresponding position and the gear motor 431 reversed. This effects a drive of the eccentric disk 441 in the opposite direction (Figure 13, arrow b) and also of the fork leg 454, rhe fork 451 and the bearing head 419 thus pivoting about the axis 420 of the head shaft 462 in the arrow direction b until the stop pin 485 meets the blocking pin 486 and blocks the adjustment. The mirror plate 411 has now reached its other end position.

Claims

**WARNING** start of CLMS field may overlap end of DESC **. arrow direction b (Figure 15) a pressure is exerted on the mirror plate 411 at the mirror edge opposite the ball 417. The mirror plate presses via the ball 480 onto the pivot lever 460 and attempts to pivot the latter about the axis of the pivot sleeve 461. Since when the gear motor 430 is stationary, due to the selflocking of the gear, the eccentric disk 440 is also non-rotatable, on this pivoting of the lever 460 the fork 450 cannot be entrained. However, the pivot lever 460 can pivot relatively to the fork 450 about the axis of the pivot sleeve 461 and change its relative angular position with respect to the fork 450 in that the static friction between the lever 460 and fork 450 is overcome, which is due to the lining disk 470. The pivot lever 460 thus slips in the region of the disk 470 with respect to the fork 450 about the axis of the pivot sleeve 461. When the gear motor 430 is again ready for operation, the mirror plate 411 is pressed manually against a rear stop 94 (Figure 15) fixed with respect to the housing and the gear motor 430 switched on by corresponding actuation of the switch so that it brings the eccentric disk 440 out of the one end position (Figure 14) by rotation in the arrow direction b into the other end position. At the latest on reaching this other end position the pivot lever 460 and the fork 450 have again reached the relative rotational position with respect to each other which they had before manual adjustment of the mirror plate 411. By corresponding switching of the switch the eccentric disk 440 is now driven in the arrow direction a so that the mirror plate 411 is pivoted by the motor in the arrow direction a or oppositely in the arrow direction b (Figure 15). The tilting adjustment of the mirror plate 411 about the axis 416 is effected in similar manner. For this purpose, the switch is correspondingly actuated, for example so that a mirror adjustment takes place in the arrow direction a (Figure 13). The eccentric disk 441 is driven in the arrow direction a and the fork leg 455 acted upon by the eccentric disk 441. The fork 451 is pivoted in the arrow direction a about the axis 420, which effects a pivoting of the bearing head 419 with guide pin 422 and thus of the mirror plate 411. The pivotal movement of the eccentric disk 441 is terminated when the stop pin 485 meets the blocking pin 487. The eccentric disk 441 is then stationary but the gear motor 431 continues to run, with reduced speed. The drive gear 434 is further driven, the static friction of the lining disk 435 being overcome, If the mirror plate 411 is to be adjusted by the electric motor in the opposite direction (dashed line in Figure 15) the switch is brought into the corresponding position and the gear motor 431 reversed. This effects a drive of the eccentric disk 441 in the opposite direction (Figure 13, arrow b) and also of the fork leg 454, rhe fork 451 and the bearing head 419 thus pivoting about the axis 420 of the head shaft 462 in the arrow direction b until the stop pin 485 meets the blocking pin 486 and blocks the adjustment. The mirror plate 411 has now reached its other end position. On failure of the adjustment via the gear motor 431 the mirror plate 411 can also be tilted manually for example into the position shown in dashed line in Figure 13. The upper edge of the mirror plate 411 is pressed and the latter pivoted via the guide pin 422, the bearing head 419 with head shaft 462 and coupling disk 463 about the axis 420. The static friction of the lining disk 465 is overcome so that the bearing heats 419 can be pivoted relatively to the fork 451 about the axis 420. When the gear motor 431 is operable again the mirror plate 411 is first pressed manually against a stop 495 (Figure 13) and the gear motor 431 then switched on for moving the eccentric disk 441 into the end position according to Figure 13 in which the bearing head and the fork 451 again assume the correct angular position with respect to each other. The two stops 494, 495 fixed with respect to the housing are arranged at the back of the mirror plate 411. They are formed for example by integral portions or housing edges. The stop 494 serves for limiting the maximum pivot angle of the mirror plate 411 when the latter is pivoted manually about the axis 415 in the arrow direction b. The stop 495 serves to limit the maximum pivot angle when the mirror plate 411 is tilted manually about the axis 416 in the pivot direction (arrow a, Figure 13). The stops 494, 495 are of significance when after failure of the gear motors 430, 431 the exact angular coupling between the fork and associated part to be driven is to be re-established. Firstly, the mirror plate 411 is pressed by pivot movement and/or tilting movement against the stop 494 and/or 495. The gear motor is then switched on in the direction which effects a power adjustment of the mirror plate in the same sense as previously effected manually. At the latest when the eccentric disk driven by the gear motor has reached its blocked end position in this drive direction of rotation the exact angular position is again obtained between the fork and the part acting on the mirror plate, i.e. pivot lever 460 or bearing head 419. Thus, special manipulations in the interior of the mirror housing and of the mirror mechanism are not necessary. WHAT I CLAIM IS: -

1. A rearview mirror for a vehicle or the like, the mirror having a housing (212, 312, 412); a mirror plate (211; 311, 411); a first joint (217, 218 etc.) connecting the mirror to the housing, said joint being spaced from the centre of the mirror towards one edge thereof,

said joint providing for tilting of the mirror about two axes perpendicular to each other, first tilting means (253) located adjacent said edge for tilting the plate about the first of said axes, second tilting means (254) located adjacent said edge for tilting said plate about the second of said axes, actuating means for moving said second tilting means including a second joint having relatively slidable members (219, 222) which move relatively to each other to permit tilting of the plate about the first axis and which connect with each other to actuate said second tilting means, electrical motor means for actuating the first tilting means and for actuating the second tilting means via the second joint; and means for mounting the housing on a vehicle bodywork so that the first axis is substantially vertical and the second axis is substantially horizontal.

2. A mirror according to Claim 1, wherein the first joint is a ball joint and the second joint is a two-axis joint disposed along the horizontal axis in spaced relationship thereto, said joints being both disposed on the back of the mirror plate, the two-axis joint comprising a bearing head (219) which is pivotally mounted on the housing (212) or on the mirror plate (211) about the horizontal axis or an axis parallel thereto (216, 220), and a guide slot (221) extending substantially perpendicular to the bearing axis (220) of the bearing head (219) and substantially horizontally, and furthermore a guide pin (222) which is aligned substantially perpendicularly to the mirror plate plane and is secured to the mirror plate (211) or the holder (212) thereof and which passes through the guide slot (221) with play in the slot direction and transversely thereof in such a manner that on a mirror plate pivoting in the ball joint (217, 218) about the substantially vertical axis (215) a relative displacement occurs between the guide pin (222) and guide slot (221) whereas on a mirror plate pivoting in the ball joint (217, 218) about the substantially horizontal axis (216) a positive coupling obtains between the guide slot (221) and guide pin (222) and a pivoting effected about the bear ing axis (220) of the bearing head (219), and that the electric motor means (251, 252; 233) acts via tilt adjusting element (254; 239) or directly on the bearing head (219) or the mirror plate (311) for tilting adjustment about the bearing axis (220) thereof and which furthermore acts via a pivot adjust ing member (253; 238) or directly on the guide pin (222) or directly on the mirror plate (311) for the pivot adjustment thereof about the vertical axis (215).

3. A mirror according to Claim 2, charac terized in that on the bearing head (219) or on the mirror plate (311) a tab (225, 325) is mounted on which the tilt adjusting member (254; 239) acts for tilting adjustment of the mirror plate (211; 311) about the substantially horizontal axis (216).

4. A mirror according to Claim 3, characterized in that the tab (225; 325) extends substantially vertically.

5. A mirror according to Claim 2, 3 or 4, characterized in that the guide pin (222; 322) is slightly arcuate in the longitudinal direction or has an arcuate chamfer (226).

6. A mirror according to any one of Claims 2 to 5, characterized in that in the guide slot (221) a spring (227) engages which in the direction of the bearing axis (220) of the bearing head (219) and transversely of the pin longitudinal direction presses against the guide pin (222) eliminating transverse slack.

7. A mirror according to Claim 6, wherein the spring is a leaf spring.

8. A mirror according to any one of Claims 2 to 7, characterized in that the return force is provided by a return spring (228) which engages the mirror plate (211) beneath the bearing head (219) and substantially in the corner region of the mirror plate (211), extends over a portion of the area extent of the mirror plate (211) and is held with its other end (230) beneath the lower mirror plate edge on the mirror plate holder (212).

9. A mirror according to any one of Claims 2 to 7, characterized in that the at least one electric motor has an output which comprises at least one eccentric cam (253, 254; 238, 239) as tilt adjusting member or pivot adjusting member which bears on the tab (225, 325) or engages the mirror plate (211; 311) directly or via a lever fixed with respect to said plate.

10. A mirror according to Claim 9, wherein the eccentric cam is constructed as cam disk (253, 254; 238, 239) with which its peripheral face bears on the tab (225; 325) or on the mirror plate (211; 311) directly or via a lever fixed with respect to said plate.

11. A mirror according to Claim 9 or 10, wherein the electric motor means is a reversible gear motor.

12. A mirror according to any one of Claims 2 to 10, characterized in that electric motor means comprises two electrical gear motors (251, 252) with eccentric cams (253, 254) driven thereby the first gear motor (251) with cam (253) being associated with the mirror plate (211) or the lever fixed with respect to said plate and serving for pivotal adjustment of the mirror plate (211) about the substantially vertical axis (215) whilst the second gear motor (252) with cam (254) is associated with the tab (225) and serves for the tilting adjustment of the mirror plate (211) about the substantially horizontal axis (216).

13. A mirror according to any one of Claims 2 to 10, characterized in that the at least one electric motor is a single reversible gear motor (233) whose output (240) acts jointly on two eccentric coaxial cam disks (238, 239), the first cam disk (238) bearing on the mirror plate (211) and the second cam disk (239) on the tab (225).

14. A mirror as claimed in Claim 13, characterized in that the cam path (242) of the second cam disk (239) increases substantially continuously radially up to the eccentricity maximum in the first output direction of rotation (arrow 243) and that (241) of the first cam disk (238) increases in this manner in the opposite second output direction of rotation (arrow 244) of the output shaft (240).

15. A mirror according to Claim 13 or 14, characterized in that the two cam disks (238, 239) are each coupled via a positive or nonpositive free-wheel (245, 246) to the joint output shaft (240), the free-wheels (245, 246) being so designed that the first free-wheel (245) associated with the first cam disk (238) transmits a torque in the first output direction of rotation (arrow 245) of the output shaft (240) and rotates freely in the opposite second output direction of rotation (arrow 244) whilst the second free-wheel (246) associated with the second cam disk (239) rotates freely in the first output direction of rotation (arrow 243) of the output shaft (240) and transmits a torque in the opposite second output direction of rotation (arrow 244).

16. A mirror according to Claim 15, characterized in that the free-wheels (245, 246) of the two cam disks (238, 239) are constructionally identical and only disposed in opposite arrangement on the output shaft (240).

li. A mirror according to Claim 15 or 16, characterized in that the two free-wheels (245, 246) are each constructed as non-positive spring or roller free-wheels.

18. A mirror according to Claim 17, charac terized in that the return stop (280) is con structed as friction brake (Figure 13).

19. A mirror according to Claim 18, where in the friction brake comprises for at each cam disk (238, 239) a friction element (289), for example a brake block or brake pin, which is stationary with respect to said disk and which by means of a spring (290) effective in the radial direction of the cam disk is pressed with its friction surface (291) continuously on a peripheral portion of the cam disk.

20. A mirror according to Claim 19, where in the return stop (280) comprises for each cam disk (238) a blocking disk (281) which is axially adjacent to said cam disk and coaxial therewith and which is centred on the output shaft (240) and mounted freely rotatably and is positively coupled by means of a driver (287) to the cam disk (238) and rotatable.

21. A mirror according to Claim 20, where in the friction element (289) engages the periphery of the blocking disk (281) or a cylindrical shaft portion of the cam disk.

22. A mirror according to any one of the preceding Claims, characterized in that on the mirror plate (411) a pivot lever (460) or bearing head (419) engages positively in the respective tilt direction but otherwise freely moveably and that the tilt lever (460) and the bearing head (419) are independently connected via a slip or friction clutch (470; 447; 463; 465; 435) to the associated adjusting means.

23. A mirror according to Claim 22, characterized in that as operative coupling in the power path between the first fork (450) and the pivot lever (460) and in the power path between the second fork (451) and the bearing head (419) in each case a slip clutch (447, 435) is disposed with preferably adjustable slip behaviour.

24. A mirror according to Claim 23, characterized in that the pivot lever (460) and the first fork (450), as also the bearing head (419) and the second fork (451), are arranged in each case on a common axis and clamped together with interposition of the respective strip clutch (470, 465).

25. A mirror according to Claim 24, characterized in that the slip behaviour is adjustable via the axial tensioning force in such a manner that the torque necessary for overcoming the static friction of the slip clutch (447, 435) is greater than that necessary for the pivot drive or tilt drive of the mirror plate (411) about the spatially substantially vertical or horizontal axis (415, 416).

26. A mirror according to any one of Claims 22 to 25, characterized in that the bearing head (419) is disposed non-rotatably on a head shaft (462) which carries non-rotatably thereon a clutch disk (463) and a slip or brake lining disk (465), and that the second fork (451) in spaced relationship with and substantially perpendicularly to the fork legs (454, 455) is traversed with clearance by the head shaft (462) and held by means of an adjusting nut (466) with interposed springs (467), preferably spring washers, on the head shaft (462) and is pressed with adjustable spring force against the slip or brake lining disk (465) and the coupling disk (463), and the mirror plate (411), when the second eccentric disk (441) and second fork (451) are stationary, is tiltable by manual actuation about the spatially substantially horizontal axis (416) by the bearing head (419) with head shaft (462) and coupling disk (463) in pivotal, overcoming the static friction of the slip or brake lining disk (465), relatively to the second fork (451) about its bearing axis (420).

27. A mirror according to any one of Claims 22 to 25, characterized in that the pivot lever (460) and the first fork (450) are mounted spaced from the fork legs (452, 453) pivotally on a pivot sleeve (461) which is pivotally moveable on a journal (424), that furthermore on the pivot sleeve (461) between the pivot lever (460) and the first fork (450) a slip or brake lining disk (470) is disposed and that the first fork (450) is adapted to be pressed by means of an adjust ins nut (471) engaging the pivot sleeve (461) wili interposed springs (472), with adjustable spring force against the slip or brake lining disk (470) and the pivot lever (460) in such a manner that the mirror plate (411) when the first eccentric disk (440) and first fork (450) are stationary is pivotal by manual actuation about the spatially substantially ver tidal axis (415) by pivoting the lever (460), overcoming the static friction of the slip or brake {ining disk (470), relatively to the first fork (450) about the axis of the pivot sleeve (461).

28. A mirror according to Claim 27, characterized in that the interposed springs are spring washers.

29. A mirror according to any one of Claims 22 to 28, characterized in that the pull-push mounting of the pivot lever (460) comprises a ball (480), at the pivot lever end and said ball bears on the back of the mirror plate (411), and a substantially angular flat spring (481) which is secured to the mirror plate back, the ball (480) being accommodated in the intermediate space which is defined by the angle leg (482) substantially parallel to the mirror plate (411) and in spaced relationship thereto on the one hand and the mirror plate back on the other.

30. A mirror according to Claim 29, wherein said ball is a plastic ball.

31. A mirror according to any one of Claims 22 to 30, characterized in that the first eccentric disk (440) with the first fork (450) and the second eccentric disk (441) with the second fork (451) each comprise an end stop means (484, 488, 489; 485, 486, 487) with associated gear decoupling (447, 435) by means of which the rotary movement of each eccentric disk (440, 441) is limitable in both drive directions of rotation (arrows a and b) to a peripheral angle of about 1800 and the respective eccentric disk (440, 441) is separable from the drive torque of the associated gear motor (430, 431).

32. A mirror according to Claim 31, characterized in that for the gear disengagement a slip clutch (447, 435) is disposed in each case between the eccentric disk (440, 441) and its drive member (446, 434) of the associated gear motor (430, 431).

33. A mirror according to Claim 32, characterized in that the slip clutch is provided with adjustable slip behaviour.

34. A mirror according to any one of Claims 31 to 33, characterized in that the slip -behaviour of the slip clutch (447, 435) is adjustable via the axial tensioning force in such a manner that the torque necessary for overcoming the static friction of the slip clutch 447, 435) is greater than the drive torque necessary for the pivot drive or tilt drive of the mirror plate (411) about the spatially substantially vertical and horizontal axes (415, 416) between the end positions.

35. A mirror according to any one of Claims 22-to 34, characterized in that each eccentric disk (440, 441) is rotatably mounted on a bush (444, 432) which is mounted on the associated gear motor (430, 431) and on said bush a drive gear (464, 434) meshing with the driven pinion (454, 433) of the gear motor (430, 431) is also mounted, that on the bush (444, 432) between the drive gear (446, 434) and the eccentric disk (440, 441) a slip or brake lining disk (447, 435) is arranged and that the eccentric disk (440, 441) is pressed by means of an adjusting nut (448, 436) engaging the bush (444, 432) with interposed springs (449, 437) with adjustable spring force against the slip or brake lining disk (447, 434) and the drive gear (446, 434) in such a manner that when the eccentric disk (440, 441, Figure 14, Figure 13) runs against one of the end stop means and is held fixed said disk may be uncoupled, overcoming the static friction of the slip or brake lining disk (447, 434), by the drive torque of the drive gear (446, 434), said gear continuing to rotate with reduced speed.

36. A mirror according to Claim 35, characterized in that each bush is rotatable on a stationary journal (426, 427).

37. A mirror according to Claim 35 or 36, characterized in that the interposed springs are spring washers.

38. A mirror according to any one of Claims 31 to 37, characterized in that each eccentric disk (440, 441) for forming the end stop means comprises on an end face, an axially projecting projection which is disposed near the outer peripheral surface and substantially on the peripheral region of greatest eccentricity.

39. A mirror according to Claim 38, characterized in that the end stop means is provided on the end face remote from the gear motor (430, 431).

40. A mirror according to Claim 38 or 39, characterized in that the axially projecting projection is a stop pin (484, 485).

41. A mirror according to any one of Claims 38--40, characterized in that the second fork (451), carries on the inside of each fork leg (454, 455) a projection substantially perpendicular thereto, the projecting length of which is so dimensioned that with its free end it projects over the path through which the stop pin (4854 travels radially up to the eccentric disk centre and when the disk (441) is pivoted in both directions of rotation (arrows a and b) through in each case about 1800 peripheral angle forms an end stop for the stop pin (485).

42. A mirror according to Claim 1, charac terized in that the projection substantially perpendicular to the inside of each fork leg is a blocking pin (486, 487).

43. A mirror according to any one of Claims 38 to 40, characterized in that for the first fork (450) two stud bolts (488, 489), fixed with respect to the housing are associated with the stop pin (484) and are disposed spaced from the disk end face remote from the gear motor (430, 431) at right angles to the disk axis of rotation on either side thereof at equal distances and lie on the track through which the stop pin (484, 485) travels when the eccentric disk (440, 441) is pivoted in both directions of rotation (arrows a and b) through in each case about 180 peripheral angle, the stud bolts (488, 489) forming with their free end face the end stop for the stop pin (484, 485).

44. A mirror according to Claim 43, characterized in that the two fork legs (452, 453) of the first fork (450) each comprise at the lower end in the front region facing the stud bolts (488, 489) a recess (490, 491) continuing up to the leg end for passage of the stud bolts (488, 489) when the fork is pivoted about its axis (461).

45. A mirror according to any one of Claims 22 to 44, characterized in that the mirror housing (412) comprises at least two stops (494, 495) which are fixed with respect to the housing and disposed at the back of the mirror plate (411), one stop (494) of which forming an end stop limiting the maximum pivot angle on manual pivoting of the mirror plate (411) about the vertical axis (415) in one direction (Figure 15, arrow b) whilst the other stop (495) forms an end stop which limits the maximum tilt angle of the mirror plate (411) on manual tilting about the substantially horizontal axis (416) in one direction (Figure 13, arrow a).

46. A mirror according to Claim 45, characterized in that the other stop (495) forms an end stop which limits the maximum tilt angle of the mirror plate (411) on manual tilting about a substantially horizontal axis (416) in one direction (Figure 13, arrow a) in such a manner that after failure of the gear motor (430, 431) and effected manual adjustment of the mirror plate (411) when the gear motors are again ready for operation (430, 431) for the operative correct angular coupling between the pivot lever (460) and first fork (450) or between the bearing head (419) and second fork (451) the mirror plate (411) may be pressed firstly manually in a pivot direction (Figure 15, arrow b) and/or a tilt direction (Figure 13, arrow a) against the associated stop (494, 495) and thereafter the associated gear motor (430, 431) may be switched on for pivot actuation or tilt actuation in the same pivoting or tilting direction until the eccentric disk (440, 441) has reached the associated end position and an accurate angular operational coupling established.

47. A mirror, substantially as described herein with reference to any of the examples illustrated by the accompanying drawing.

48. A mirror according to Claim 1, substantially as hereinbefore described.