WO1991012158A1

WO1991012158A1 - Windshield wiping apparatus

Info

Publication number: WO1991012158A1
Application number: PCT/US1991/000960
Authority: WO
Inventors: Gregory John Owoc
Original assignee: Gregory John Owoc
Priority date: 1990-02-13
Filing date: 1991-02-12
Publication date: 1991-08-22

Abstract

A windshield wiping apparatus (1) which includes a wiper blade assembly (2) carried by either a sliding stem or sliding sleeve means (24) which reciprocates in a longitudinal direction upon a rigid sleeve means (24) is also oscillated by an oscillating shaft (10) in an arcuate wiping path across an automotive windshield (3). A precisely contoured wiping path (11) is achieved by utilizing either one of two preferred embodiments. The first embodiment uses a planetary drive gearing means to effect an additional, secondary oscillation rate in an oscillating pinion (58) that longitudinally reciprocates a unique rack gear (7), also known as a mangle gear. The second embodiment uses a planetary drive gearing means to effect uniform oscillation of a pinion (105) that drives a unique rack gearing means, a special mangle gear (94) that effects an additional, secondary longitudinal reciprocating motion of itself, being driven in a first, rectilinear path that reverses into a second, generally rectilinear opposite path. Both embodiments reciprocate said sliding stem or sliding sleeve means (24) during wiping apparatus' oscillation cycles so as to effect a contoured wiping path.

Description

WINDSHIELD WIPING APPARATUS

BACKGROUND OF THE INVENTION

The present invention relates to a windshield wiping apparatus including a wiper blade assembly driven in a longitudinally reciprocating motion on a sliding sleeve or stem means that arcuately oscillates across an automotive windshield with a precise contouring path.

There are windshield wiping apparatuses that effect this longitudinal reciprocating motion to achieve a contoured wiping path. One such is described in U.S. Pat. No. 4,447,928 wherein a crank drive acts to reciprocate the wiper stem during an arcuate oscillation stroke. Another is described in U.S. Pat. No. 4,649,590 wherein a lever mechanism imparts longitudinal reciprocation to a wiper stem that is guided by rocking levers and coupling rod arrangement. Still another is described in U.S. Pat. No. 4,630,327 wherein a single crank, guided by the lower area of a telescopic wiper stem, comprises two pinions, two internal ring gears and two axis means in an eccentric gearing arrangement to achieve the above reciprocating motion.

The present invention utilizes a novel method to gain effective rectilinear reciprocating advantage by means of rack gearing. Until the present invention the rack gearing drive principle was known only for effecting either an arcuate windshield wiper oscillation, as described in U.S. Pat. No. 1,510,015 wherein a rack gear oscillates a pinion non-rotatatly affixed to the bottom of an arcuately oscillating wiper stem, or rack gearing effecting a lateral reciprocation of a wiper stem and base across an automotive windshield, which is known in U.S. Pat. No. 1,746,528. However, the present invention introduces the rack gearing principle to longitudinally reciprocate a wiper blade assembly during arcuate oscillation across an automotive windshield and achieves a highly contoured path through a relatively simple apparatus.

SUMMARY OF THE INVENTION The object of the present invention is to provide windshield wiping oscillat that utilizes compound motion, that is, oscillation of the wiper stem as well as reciprocating extension and retraction of the stem during wiping oscillation cycles. This may be accomplished through a various multiplicity of rack gearing arrangements.

The apparatus as such would comprise first and second preferred embodiments and should provide at least the following seven following advantages: 1. A smooth transmission of reciprocating motion of a sliding wiper stem or sleeve, given the deliberate gradating flow potential inherent in reciprocating reck gearing mezns; this opposed to the jolting or jerking type of reciprocation associated with some types of eccentric drive means.

2. A low number of moving parts promoting constancy of gear mesh as well as uniform wear dissipation.

3. The fact that the rack gear is the drive means for the extending portion of the apparatus, and both rack gear and extending portion both extend in the same axial plane offers a clear advantage for wiping those windshields possessing a high width to height ratio.

4. Capable, simple structure modifications whereby a broad range of adaptability in contouring windshields is available, for instance: The first embodiment may introduce an additional, secondary oscillation rate into a pinion that would drive the above said Vack gearing means, as will be discussed. The second embodiment simply alters the shape of the rack gearing means, achieving a similar contour.

5. Relative ease of lubrication since gearing means tend to distribute lubricants more constantly and evenly. Gearing means may be made compact also, thus simplifying sealing the drive means.

6. Low Visibility Obstruction: In the first embodiment the two lobate extremltied rack gearing means, called mangle gearing or a mangle gear, can remain quite narrow, even while accomodating an oscillating drive pinion. This allows the oscillating stem and any applicable sliding member, even including a protective sheathing means to still remain relatively narrow in structure.

7. The achievement of eliminating a second wiper assembly and drive means, even though the present invention involves more manufacturing steps and parts, offers obvious advantages as well. Two preferred structures, the first and second preferred embodiments, utilize a rack gearing means that may achieve the above advantages. This rack gearir.g means is further defined as a mangle gearing means, "mangle gearing" being defined by McGraw Hills "DICTIONARY OF SCIENTIFIC AND TECHNICAL TERMS", 4th Ed., 1989, as follows, "Gearing for reciprocating motion; a pinion (when) rotating in a single direction drives a rack (gearing means) with teeth at the end and on both (any) sides." [Parenthetical words added] It is obvious that the rever sing characteristics of the mangle gear make it ideal for this rack gearing application. In the present invention, rack gearing and mangle gearing will extend to but not be limited to the above definition since rack gearing principles that extend beyond the scope of the definition will be utilized in the present invention. For instance, the reversing characteristics necessary in second preferred embodiment are not well covered by the above definition.

The first preferred embodiment utilizes a single mangle gear affixed to a sliding sleeve or sliding stem. This mangle gear is driven by a pinion that oscillates causing the mangle gear to longitudinally reciprocate, that is, to linearly retract and extend a given distance that depends primarily on the length of the mangle gear and to a somewhat lesser extent on its contour. The rate of said longitudinal reciprocation would depend upon the oscillating velocity of the said drive pinion during the arcuate wiping stroke of the apparatus. Lobate extremities, also defined as generally curve-shaped mangle gear direction change points are where the pinion drivingly passes through displacing the mangle gear in a reversed rectilinear, or straight line direction, and its respective sliding member. First and second embodiments comprise a double pinioned shaft wherein one pinion on the said shaft drives the mangle gear while the opposite pinion is drivingly attached to a planetary drive means further comprising a third gearing means that is called a sector gear which may be stationary or partially oscillatable, depending upon the desired contour wiper stroke. To make the sector gear partially oscillatable a fourth gearing means is provided whereby the sector gear would be driven into rotatation toward the direction of oscillation stroke at a specific phase or phases during the same stroke. At the moment this began the oscillating double pinioned shaft would begin a slower oscillation; this in turn would cause the mangle gear to slow its retraction or extension of the sliding member during specific wiper oscillation phases and this in turn would allow a potential for precise contouring by the wiper blade of the windshield's perimeter, including both flared sides.

In this first preferred embodiment, it is to be understood that instead of using the fourth said gearing means to partially oscillate the said sector gear, various other means may be used to accomplish the same such as by mutilated gearing comprising, for instance, intermittent gears or sector gears. Elliptical gearing, a bar linkage apparatus or a cam driving means may substitute for said fourth gearing, accomplishing the same result. A chain and sprocket means may be arranged to drive said mangle gear, also. The second preferred embodiment utilizes even less gearing means to accomplish the same contour by a special mangle gear chat requires no additional, secondary oscillation of its drive pinion. Instead, due to its unique, generally rectilinear contour, the mangle gear effects an additional, secondary, generally longitudinal reciprocation of itself as it is driven by its oscillating pinion in a first rectilinear gear path whereby the mangle gear's generally rectilinear driving direction is reversed in a second path as first preferred embodiment's said mangle gear, that is, through said lobate extremities. However, the drive pinion for this special mangle gear, upon entering the said lobate reversing extremities begins to drive the mangle gear in a reversed, generally linear arced or curved path that causes the pinion to expend an equal or near equal amount of revolutions as expended in the prior, opposite path but with the result that an unequal, preferably less, absolute, rectilinear distance is traveled in this latter, said curved path. This difference in absolute linear distances traveled by these reciprocating pcths determines how far and at what point during the wiping oscillation stroke the reciprocating, sliding member will extend and retract said wiping assembly. This in turn wculd allow a potential for precise contouring by the wiper blade of the windshield's perimeter. The additional, slight visual obstruction caused by the necessarily wider mangle gear used may be alleviated by lowering the central pivot point of the wiping apparatus to cover more of the said sliding member, that is, sliding sleeve or sliding stem. The invention as summarized may be more thoroughly understood by reviewing the following detailed description and drawings.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a longitudinal cross-section of the windshield wiping apparatus shown in upright position upon the verticle middle of an automotive windshield at the oscillation point mid-way through a clockwise or counter-clockwise wiper oscillation stroke.

Fig. 1A is a frontal perspective from outside the automotive vehicle illustrating basic outlines of major wiping apparatus' elements in relation to the automotive windshield.

Fig. 1B isa top perspective as viewed downward from the roof of the automotive vehicle.

Fig. 2 is a positional diagram illustrating various potential wiping apparatus' contour sweeps when using a gearing means to drive a simple rectilinear mangle gear having two lobate extremities.

Fig. 2A is frontal perspective cutaway of Fig. 2's simple mangle gear on a sleeve means sliding upon a stem means approximately mid-way through a clockwise or counter-clockwise wiper oscillation stroke.

Figures 2B, 2C, 2D in order comprise individual positional diagrams of the wiping apparatus as it continues all the way through the latter half of a clockwise oscillation stroke. Illustrated also are the positions of various gear, flange and spring means during the same stroke.

Fig. 3 is a positional diagram illustrating a potential wiping apparatus contour sweep when using a gearing means to drive a special rectilinear mangle gear that reverses path direction at more than two lobate extremities.

Fig. 3A and 3B are frontal perspectives of the second embodiment including two special rectilinear mangle gears that reverse rectilinear path direction at more than two lobate extremities, effecting a contour sweep similar to that which is illustrated in Fig. 3.

Fig. 3C illustrates a simple rectilinear mangle gear that effects a contour sweep similar to that which is illustrated in Fig. 2. This particular mangle gear comprises gear teeth running back to back down a mid-positioned rectilinear reversing rack.

DETAILED DESCRIPTION

In describing the preferred embodiments of the invention illustrated in the drawings and summarized above specific terminology will be resorted to for sake of clarity. However, it is not intended to be limited to the specific terms so selected and it is to be understood that each specific term includes all technical equivalents which operate in a similar manner to accomplish a similar purpose.

In Fig. 1 a comprehensive cross-sectional illustration depicts wiping apparatus 1 mid-position through either a clockwise or counterwise arcuate oscillation stroke. Said wiping apparatus 1 utilizes a rack gearing means futher defined as a mangle gear 7, hereinafter also referred- to as MG7. Figs. 1, 1A, 1B, 2, 2A, 2B, 2C, 2D, and 3C all illustrate said MG7 in various views and facets of operation in a first of two preferred embodiments wherein a wiper blade assembly 2 with an assembly stem back means 46 supports a wiper blade clip 43; said clip 43 supporting a slidable back support 45 which adheres to a flexible windshield

wiper piece 44 which wipes an automotive windshield 3. Said assembly 2 is attached to protruding sliding sleeve extremity 35 upon hinge pin 37 through means of wiper blade assembly hinge piece 36. Sliding sleeve 24, hereinafter also referred to as SS24 comprises a water stop piece 33 wherein water is prevented from entering wiping apparatus 1 if said sleeve extremity 35 is hollow in structure. SS24 comprises a protective sheathing piece 34 which protectively sheathes linearly protruding, second protective housing shroud piece 22 preventing foreign matter, including water from entering wiping apparatus 1 both during longitudinal recipro- eating extension and retraction of SS24 and throughout wiping apparatus' 1 oscillation cycles. Said housing shroud piece 22 comprises lower portion protective shroud 21 which is fastened preferably through a bolt or rivet means to the bottom end of rigid stem means 23, hereinafter also refexred to as RS23, at lower portion housing shroud support bolt 48 and to rigid stem means' cross member 29 at second housing shroud front support bolt 28.

Second protective housing shroud 21 oscillates with respect to a first protective housing shroud 20 wherein both said shrouds may be modified to protectively shroud any of the invention's embodiments. Said driving means of first embodiment is further illustrated in Fig. 1 wherein oscillation motor 4 drives an oscillating shaft 10 that is rigidly attached to said rigid stem means 23; oscillating shaft 10 further comprises shaft hinge 11 comprising hinge pin 12 and allowance curvature 13. Allowance curvature 13 permits wiper assembly 2 sliding access below shaft's 10 horizontal position; said RS23 further comprises a ballbearing groove 30 along both sides wherein ballbearings 26 held within said groove 30 by wraparound ballbearing support 25 enable SS24 to longitudinally reciprocate on RS23. SS24 further comprises at upper end, sliding sleeve ballbearing grooves 65 wherein additional ballbearings 27 spin while positionally retained in rigid stem's 23 ballbearing supports 31. Said SS24 further comprises wraparound securing flanges 32 which may be stamped metal that is bent to securing positions in assembly; said securing flanges 32 keep back and front side of SS24 snug upon RS23 throughout wiping apparatus' 1 oscillation cycles.

When said oscillating shaft 10 arcuately oscillates RS23 through a wiping path across automotive winduhield 3, the shaft portion of double pinioned

shaft 57, being rotatably postitioned in RS23's double pinioned shaft support means 55, positions its second pinion 56 into continuous mesh with an internal ring gear sector 63, hereinafter also referred to GS63. Said GS63 effects an oscillating motion in said second pinion 56 as RS23 arcuately oscillates through clockwise and counter-clockwise strokes driving said double pinioned shaft 57 to oscillate the first pinion 58 of said double pinioned shaft as well. Said first pinion 58 oscillates in mesh with said mangle gear's 7 teeth, displacing said MG7 in a rectilinearly reciprocating motion. Fig. 2A illustrates detailed frontal perspective cutaway of MG7 and associated drive means wherein MG7's pinion shaft guide 76 constantly presses said double pinioned shaft 57 against itself and against inner wall 103 keeping said first pinion 58 in mesh with MG7's teeth during pinion oscillation. Said pinion shaft guide 76 is rigidly affixed to MG7's housing cap means (see: 112, Fig. 3C). MG7 further comprises two reversing curve or lobate extremities similar to those depicted in 130x and 130y, Fig. 3C whereat elongated hinge aperture guides 60, 61 are rigidly affixed. Said SS24 comprises rigidly attached pms 70, 71 which art received by said hinge aperture guides 60, 61 in a laterally reciprocating path. Said MG7 thrusts forward and tugs backward upon said pins 70, 71 effecting reciprocating extension and retraction of SS24 upon RS23. SS24 further comprises an inner guide slot 119 for reciprocatively

receiving said double pinioned shaft 57 while SS24 reciprocates on RS23.

Note Fig. 2 wherein various wiping paths on windshield 3 possessing windshield perimeter 68 are divided into four 45° quadrants and are designated by Roman

Numerals I-IV beginning clockwise from 180° to 0° and wherein MG7's position is depicted at various oscillation phases I-IV as it would appear through either a 180° clockwise or 180° counter-clockwise wiping apparatus 1 oscillation stroke. "A" (solid line) represents the windshield surface area wiped through a single oscillation stroke using no reciprocating means to extend or retract the wiper blade assembly 2. Oscillation stroke "B" (dotted line/slash-dot top line) represents a single stroke using mangle gear 7 and a stationary GS63, that is, wherein MG7 retracts at the same rate it extends. Note: Arrangement effecting "B" stroke may result in an acceptable wiping contour stroke using only the required two and one half gear pieces, that is, a half gear sector, a double pinioned shaft

and a mangle gear. "H" (slash-dot line) represents the preferred contour sweep and may be achieved by introducing an additional, secondary oscillation rate into the mangle gear drive pinion 58, preferably in the present invention by partially oscillating said gear sector 63 in the same direction as the oscillation stroke but at a different, preferably slower rate. Note: It is obvious that flanges could easily trip GS63 to begin oscillating at the same rate with oscillating shaft 10, however this would result in generally undesirable oscillation stroke "M", that is, the stroke resulting when MG7 remained extended at its maxima, extension length "e'", beyond approximately 135° in a clockwise stroke and beyond less than 45° in a counter-clockwise stroke. Partial, -periodic oscillation of GS63 to achieve preferred stroke "H" can be accomplished by obvious and various means, some of which were discussed in the above summary. However, the preferred method in the present invention comprises a simple velocity changing gear arrangement wherein, noting Fig. 1 and especially Figs. 2A-2D, GS63 further comprises another external gear sector 64 affixed arcuately within GS63 and wherein an external double fourth gear comprising one first larger gear 53 and one second smaller gear 77 oscillates on its own independent shaft 54 wherein said shaft 54 is rigidly attached to said first housing shroud's 20 reinforcement means 19 and wherein said smaller gear's 77 teeth constantly engage gear teeth of said external gear sector 64 and wherein said larger gear 53 constantly engages an additional, partially ocillatable double-flanged, sector third gear 9; said flanged sector third gear comprising first and second gear trip flanges 50A, 50B, respectively.which point inward toward said oscillating shaft 10 from within the inside of said sector third gear's 9 gear walls 78; said oscillating shaft 10 further comprises an engagement flange 51 which will contact the first said gear driving trip flange 50A as said shaft 10 moves through a clockwise wiper oscillation stroke beginning at approximately 45° and ending at 0°; said engagement flange 51 will contact the second said gear driving trip flange 50B through a counter-clockwise wiper oscillation stroke beginning at approximately 135° and ending at 180°. Illustrated in Figs. 2B-2D is the latter half of said clockwise stroke beginning at 90°, in Fig. 2B and finishing at 0° in Fig. 2D. In Fig. 2C, engagement flange 51 first contacts said first trip flange 50A whereat, noting Fig. 2 also, said mangle gear's 7 position is at a maximum extension wherein "e" represents the length of MG7 and "e"' represents the maximum extension length of the wiping apparatus 1; said extension length "e'" located at approximately 45°, ending wiping phase III and beginning wiping phase IV. In Fig. 2 note MG's 7 position at 0° shown partially retracted (rather than fully retracted) due to the secondary, slower, oscillation rate introduced into MG's 7 double pinioned shaft 57 pinion 58 beginning slower rate when said engagement flange 51 begins contacting said flange 50A whereby said flanged sector gear 9 begins to rotate in a clockwise direction driving said larger first gear 53 and said smaller gear 77 both in a counter-clockwise direction whereby said gear 77 drives said gear sector 64 and said GS63 in a clockwise rotation which is slower in velocity, approximately half, of said oscillation shaft's' velocity, allowing said MG7 to retract slower and wipe a greater percentage of

windshield surface area in said stroke phases I and IV. In these same phases opposite oscillation strokes effect the same return wiping pattern as the said gear trip flanges 50A, 50B are gradually released. Stiff, stabilizing, anti-backlash springs 72A, 72B join said GS63 with said flanged gear sector 9

so that during oscillation strokes wherein all said gear flanges remain unengaged, viz., during oscillation strokes froir 135°-45°, GS63 is not oscillated by the frictional drag applied by said rigid stem 23 and said double pinioned shaft 57 as they together move upon GS's63 gear teeth. Said anti-backlash springs 72A, 72B also serve to recover said GS63 on reversing oscillation strokes always toward a syuetrically upright position as well as acting as a gear shock buffer means if said wiper assembly 2 were to be suddenly obstructed during a stroke. A buffer means as such, however would preferably be adjunct to a primary buffer system built into the said oscillation motor 4. A rigid sleeve 52, around said oscillating shaft 10, supports said flanged sector third gear 9 and supports GS's63 annular support portion 8 whereby oscillating shaft 10 becomes one independent inner oscillating axis and said rigid sleeve 52 is a rigid, second independent outer axis whereby said sector third gear 9 and GS63 can both oscillate independent of one another and independent of said oscillating shaft 10.

Fig. 3B illustrates special rectilinear mangle gear 94 hereinafter also referred to as SMG94 which is driven by second pinion 105 of double pinioned shaft 108; said double pinioned shaft 108 is driven by oscillating pinion 104 as said shaft 108 is oscillatedby stationary external gear sector 101 through arcuate oscillating drive motion of said RS23. SMG94 further comprises curved gear reversing points called gear lobate extremities 120x, 120y, 120z whereby SMG94 rectilinearly, or in a generally straight direction reverses itself as it is driven by pinion 105; said double pinioned shaft 108 passes through

SMG's94 guide slot 99 always being kept snug and in mesh by walls of inner shaft guide 98. SMG 94 both laterally reciprocates and reciprocatively pivots in hinge aperture guide 60 on hinge-pin 73 rigidly attached to said SS24.

Spring 97 connects SMG94 to SS24 at connecting piece 96. Said spring 97 serves to stabilize SMG94 from making a jerking motion as it is rapidly driven during wiper oscillation cycles. In Fig. 3 SMG94 has length "z" and maximum extended wiping length "z"' at approximately 135° and 45° wiper oscillation positions. Considering a counter-clockwise stroke, note SMG94 at a 180° rest position, having moved 45° counter-clockwise from the 135° point and yet remaining only partially retracted, which partial retraction effected an absolute rectilinear retracted distance that was less than the absolute rectilinear extended distance. Said oscillating pinion 105 did not change velocity or necessarily revolve less times but SMG94 was diverted during phase I and IV by lobate extremities 120x and 120y that drove SMG94 into a generally rectilinear path that was equal in number of mangle gear teeth 100 expended to that number of mangle gear teeth 100 expended during wiper oscillation phases II and III; thus allowing a variation in the rate said SS24 reciprocatively retracts and extends, which in turn would result in the same preferred contour sweep "H" in either Fig. 2 or 3. If stationary gear sector 101 were to be made partially oscillatable, as in first preferred embodiment, SMG94 might be used to achieve wiping a highly irregular windshield contour. effectively.

Finally, note Fig. 1 and Fig. 1B, wherein torsional spring means 16, 14 respectively, are attached to firewall 142, adjacent to front of dashboard 6. Said spring means 16, 14 exert a torsional effect toward windshield 3 through hinge 11 and hinge pin 12. It should be obvious to one skilled in the art that a similar torsional spring and hinge means may be attached instead to said SS24 at or near said water stop piece 33 causing substantially the sane effect.

It is to be understood that the form of the invention herewith shown and described above and following is to be taken as preferred embodiments. Various changes may be made in the shape, size and arrangement of parts, for example: other equivalent elements may be substituted for those illustrated and described herein, parts and elements may be reversed and certain features of the invention may be utilized independently of the use of other features, all without departing from the spirit or scope of the invention, as defined in the subjoining claims.

Claims

By the Grace of God, I claim:

1. A windshield wiping apparatus for wiping the windshield of an automotive vehicle comprising:

a. A wiper blade assembly operatively connected to a sliding sleeve means; b. A rigid stem means to slidably receive said sliding sleeve means and said wiper blade assembly; said rigid stem means drivingly connected with an oscillating shaft means;

c. A primary drive means to oscillate said oscillating shaft means;

d. A planetary drive means operatively connected with said rigid stem means; e. A rack gearing drive means operatively connected with said planetary drive means and drivingly connected to said sliding sleeve means so as to effect longitudinal reciprocating motion of said sliding sleeve means and said wiper blade assembly upon said rigid stem means during wiping oscillation cycles of said windshield wiping apparatus.

2. A windshield wiping apparatus for wiping the windshield of an automotive vehicle comprising:

a. A wiper blade assembly operatively connected to a sliding sleeve means; b. A rigid sleeve means to slidably receive said sliding stem meant; and said wiper blade assembly; said rigid sleeve means drivingly connected with an oscillating shaft means;

c. A primary drive means to oscillate said oscillating shaft means;

d. A planetary drive means operatively connected with said oscillating shaft means;

e. A rack gearing drive means operatively connected with said planetary drive means and drivingly connected to said sliding stem means so as to effect a longitudinal reciprocating motion of said sliding stem means and said wiper blade assembly upon said rigid sleeve means during wiping oscillation cycles of said windshield wiping apparatus.

3. A windshield wiping apparatus for wiping the windshield of an automotive vehicle comprising:

c. A primary drive mea-is to oscillate said oscillating shaft means; d. A planetary drive means operatively connected with a rack gearing drive means; said rack gearing drive means drivingly attached to said sliding sleeve means so as to effect a longitudinal reciprocationg motion of said sliding sleeve means and said wiper blade assembly upon said rigid stem means during wiping oscillation cycles of said windshield wiping apparatus.

4. The apparatus as recited in claims 1, 2, or 3 wherein said rack gearing drive means is a mangle gear drive means further comprising a mangle gear possessing an elongated pattern; said elongated pattern describing the contour of a rectilinear gear, rectilinearly reversing direction at both lobate extremities; said lobate extremities being hingedly connected and further drivingly connected by a driving pin; said driving pin being rigidly connected to a sliding sleeve means; said driving pin slidably receiving said mangle gear's lobate extremities in a laterally reciprocating movement by means of an elongated hinge aperture guide.

5. The apparatus as recited in claims 1, 2, or 3, wherein said rack gearing drive means is a mangle gear drive means further comprising a mangle gear possessing a pattern describing the contour of a generally elliptical internal ring gear wherein said mangle gear reverses rectilinear direction at three lobate extremities and wherein two of the said three reversing directions define at least two general arcs bowed in the same direction.

6. The apparatus as recited in claim 5 wherein said planetary drive means further comprises a stationary planetary gear sector rigidly connected to a stationary sleeve means; said stationary sleeve means rigidly connected with a second protective housing shroud and further circumscribing said oscillating shaft means; either one of both said mangle gears being futher oscillatingly driven by the first of two pinions of a double-pinioned shaft wherein said double-pinioned shaft is rotatably positioned in said rigid stem means; the second pinion of said double-pinioned shaft being drivingly connected with said planetary gear sector; said windshield wiping apparatus further comprising a first moveable protective housing shroud encompassing said mangle gear whereby said first housing shroud and respective mangle gear may oscilate in a limited pendulum swing motion upon a pin rigidly connected to said sliding sleeve means; said pin being located within at least one said gear lobate extremity's elongated hinge aperture guide; said mangle gear comprising at least one other gear lobate extremity having a resilient component operatively connected, first, with said gear lobate extremity and secondly, with said sliding sleeve means; said mangle gear further comprising a shaft inner guide slot wherein guide walls of said slot apply a sufficient, continuous pressure to said double-pinioned shaft as said first pinion meshes with said said mangle gear, and as said second pinion meshes with said stationary planetary gear sector.

7. The apparatus as recited in claim 4 wherein the said planetary drive means comprises a planetary gear that oScillatingly drives a double-pinioned shaft; said double-pinioned shaft being rotatably positioned in said rigid stem means whereby one pinion of said double-pinioned shaft is oscillatingly driven by said planetary gear and the opposite end of said double-pinioned shaft comprises the oscillating pinion for driving said mangle gear in a generally longitudinal reciprocating motion; said mangle gear further comprising a shaft inner guide slot; guide walls of said slot applying a sufficient, continuous pressure to said double- pinioned shaft as the first pinion of said double-pinioned shaft meshes with said mangle gear and the second pinion of said double-pinioned shaft meshes with said planetary gear; said mangle gear's elongated pattern further describing the contour of a rectilinear internal ring gear.

8. The apparatus as recited in claim 4 wherein said planetary drive means comprises at least a stationary gearing means and an oscillating gear means;

said oscillating gear means driving said mangle gear in a rectilinearly reciprocating motion; said mangle gear being further drivingly connected with rectilinearly reciprocating, said sliding sleeve means.

9. The apparatus as recited in claim 8 wherein said stationary gearing means remains stationary through only part of the wiper oscillation cycle whereby a mutilated gearing means further comprising a sector gear drivingly connects to said oscillating gear means; said oscillating gear means

further comprising an oscillating double-pinioned shaft wherein the first pinion of the said double-pinioned shaft drives said mangle gear; said sector gear being further drivingly connected to a second mutilated gearing means whereby said sector gear is afforded limited, periodic oscillation during wiping oscillation cycles; said double-pinioned shaft's second pinion being oscil latingly driven at an additional, secondary variable rate by periodically oscillating, said sector gear; said double-pinioned sahft is first pinion driving said mangle gear in an additional, secondary, variable rectilinearly reciprocating motion; said mangle gear further driving said sliding sleeve means in an additional, secondary, variable rectilinearly reciprocating motion during wiping oscillation cycles.

10. The apparatus as recited in claim 7 wherein said planetary gear comprises an internal ring gear sector positioned arcuately about a second planetary gear sector; said second gear sector being rigidly secured within said first gear sector and arcuate about a periodically oscillating, third gear sector;

said third gear sector arcuate about said oscillating shaft means and further comprising first and second gear-driving trip-flanges radially extending from inner gear walls of said third gear sector; said oscillating shaft means further comprising an engagement flange contacting said first gear-driving trip-flange through a clockwise wiper oscillation stroke beginning at approximately 45 degrees and contacting said second gear-driving trip-flange through a counterclockwise wiper oscillation stroke beginning at approximately 135 degrees;

said windshield wiping apparatus further comprising a fourth double-gear oscillating around an axis independent of said oscillating shaft means while continuously engaging both said second and third gear sectors; said fourth double-gear driving said second gear sector during said periods of said engagement flange's and said trip-flanges' contact; said double-pinioned shaft's second pinion being oscillatingly driven at an additional, secondary variable rate by periodically oscillating, said internal ring gear sector; said double- pinioned shaft's first pinion driving said mangle gear in an additional, secondary, variable rectilinearly reciprocating motion; said mangle gear further driving said sliding sleeve means in an additional, secondary, variable rectilinearly reciprocating motion during wiping oscillation cycles.

11. The apparatus as recited in claim 10 wherein said internal ring gear sector is further operatively joined to said third gear sector by means of stiff, stabilizing, anti-backlash springs; said internal ring and third gear sectors being further rotatably joined around a housing sleeve wherein a portion of said housing sleeve circumscribes a portion of said oscillating shaft means; said housing sleeve being rigidly joined within a first protective housing shroud; said fourth double-gear being rigidly, rotatably fixed to said first protective housing section at back frame housing shroud reinforcement means.

12. The apparatus as recited in claim 11 wherein said rigid stem means comprises a rigidly connected cross member supporting a second protective housing shroud; said second protective housing shroud and respective components being oscillatable with respect to said first protective housing shroud; said first protective housing shroud being resiliently connected to automotive firewall by a torsion spring means; said housing sleeve portion further comprising an allowance aperture for said oscillating shaft mean's engagement flange to oscillate through; said oscillating shaft means further comprising a hinge means affording said windshield wiping apparatus a forward-backward swing motion; said wiper blade assembly being extended toward said windshield in a continuously pressured position upon said windshield by means of said torsion spring mean's torsional effect upon said oscillating shaft mean's said hinge means.

13. The apparatus as recited in claim 12 wherein said sleeve means further comprises a protective, secondary sleeve sheathing a portion of second said protective housing shroud during said windshield wiper oscillation cycles;

said sliding sleeve means further comprising a ballbearing means to slidably receive, respectively, said rigid stem means; said oscillating shaft means further comprising an allowance aperture permitting retracted said wiper blade assembly an increased retraction distance through said allowance aperture.

14. The apparatus as recited in claim 4 wherein said sliding sleeve means comprises a spring and hinge apparatus whereby said wiper blade assembly meets said windshield in a continuously pressured position throughout said wiping oscillation cycles of said windshield wiping apparatus.