GB1568898A - Creación de Inventos y Patentes con Inteligencia Artificial

GB1568898A – Standardpitch gearing
– Google Patents

GB1568898A – Standardpitch gearing
– Google Patents
Standardpitch gearing

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Publication number
GB1568898A

GB1568898A
GB48858/77A
GB4885877A
GB1568898A
GB 1568898 A
GB1568898 A
GB 1568898A
GB 48858/77 A
GB48858/77 A
GB 48858/77A
GB 4885877 A
GB4885877 A
GB 4885877A
GB 1568898 A
GB1568898 A
GB 1568898A
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United Kingdom
Prior art keywords
tooth
teeth
pitch
gearing
gear
Prior art date
1977-03-16
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)

Expired

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GB48858/77A
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Individual
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1977-03-16
Filing date
1977-11-23
Publication date
1980-06-11

1977-11-23
Application filed by Individual
filed
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Individual

1980-06-11
Publication of GB1568898A
publication
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patent/GB1568898A/en

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Expired
legal-status
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Current

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bending
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Steel
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diminishing effect
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Classifications

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL

F16H—GEARING

F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms

F16H55/02—Toothed members; Worms

F16H55/08—Profiling

Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS

Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC

Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION

Y10T74/00—Machine element or mechanism

Y10T74/19—Gearing

Y10T74/19949—Teeth

Y10T74/19963—Spur

Y10T74/19972—Spur form

Description

PATENT SPECIFICATION ( 11) 1 568 898
0 ( 21) Application No 48858/77 ( 22) Filed 23 Nov 1977 ( 19) g ( 31) Convention Application No 778260 ( 32) Filed 16 Mar 1977 in ( 33) United States of America (US) ‘ @ o ( 44) Complete Specification Published 11 Jun 1980 n ( 51) INT CL F 16 H 55/08 ‘ _ ( 52) Index at Acceptance F 2 Q 7 H 5 C ( 54) STANDARD-PITCH GEARING ( 71) I, WILLIAM SPENCE ROUVEROL, P O Box 9122, Berkeley, Ca 94709, U S A.
Citizen of the United States of America, 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:-
Involute gearing is essentially a standard tooth-number system of gearing That is to say, if 5 the tooth profiles of a set of gears are of the involute form, there is a certain number of teeth on the pinion that will give the set the maximum torque capacity and if the pinion has any other number of teeth, the torque capacity will be less than optimum This particular number of teeth, which may be found be simultaneous solution of the equations for surface stress and root stress, is called in this specification the «critical number of teeth» (ncr) For hardened 10 steel or plastics, ncr is in the range 15 to 25, depending on pressure angle and gear ratio; for unhardened steel or cast iron the range is usually 25 to 40, or at most 50.
The reason conventional involute gearing has a «critical number of teeth» is evident from Figure 7 of U S Patent No 3,881,364: Torque capacity plotted as a function of the number of teeth on the pinion gives a curve of diminishing ordinate in the case of tooth bending strength 15 and a curve of increasing ordinate in the case of tooth surface strength These two curves intersect to produce a two-part curve that defines the torque capacity for various pinion tooth numbers N 1 Since the two curve parts meet at a cusp, capacity falls off rapidly for values of N 1 lower or higher than ncr, and for values of N l several times as large as ncr, will be only a fraction of the maximum torque capacity at ncr This is because the Lewis equation, which is used to 20 calculate the bending strength of all involute gearing, includes the tooth module in the numerator.
The object of the invention is therefore to provide a system of gearing that will not require the tooth size to be increased as the gear size increases Since the pinion of gear sets embodying the invention can have as many teeth as desired without sacrifice of torque 25 capacity, then tooth pitch can be standardized instead of tooth number, and the great advantages of fine teeth (lower operating noise and reduced friction, heating and wear) can be made available for gears of all sizes.
The means to achieve this and other objects and advantages of the invention will be evident from the drawing as explained in the specification that follows 30
The drawing is an enlarged partial section of a pair of mating gears taken perpendicularly to the common pitch element and showing mating profiles embodying the invention.
In detail and referring to the drawing, typical teeth 11, 13 embodying the invention are shown in transverse section engaged at pitch point P Tooth 11 is on the smaller gear 12 (pinion) and has a working profile of circular arc form, the radius of the arc being r, and the 35 arc center being at T 1 Similarly, tooth 13 is on the larger gear 14 and has a circular arc working profile or radius r 2 centered at T 2 The line Q O Q 2 is the pressure line making an angle 0, called the transverse pressure angle, with a line 15 tangent to the pitch circles 16, 17 of the mating gears 12, 14 The points Q, and Q 2 are the points where the pressure line Q 1 Q 2 is tangent to the base circles (not shown) from which involute profiles would have been 40 generated (Other parts of the two gears 12 and 14, such as hubs, webs, rims, keyways, etc, are standard and are omitted in the interest of clarity) One of the distinguishing features of the gearing herein disclosed is that the radius of relative curvature r of the tooth profiles, which is expressed by the formula 45 4 1,568,8982 r= 1 1 rl r 2 is substantially smaller than that of involute gearing In involute gearing the radius of relative 5 curvature of the teeth in the transverse plane will be found to be equal to:
G ri = RI( -+G)sin k ( 2) where R is the pitch circle radius of the pinion G is the ratio of the pitch circle radii of the gear and pinion, and 0 is the pressure angle in the transverse plane The radius of relative 10 curvature r at the pitch point for gearing embodying the invention is nearly always less than % of the value or ri given by Equation 2, and in most cases gearing falls into the range between 20 %and 60 %or ri On the other hand, the radius r will always be greater than about 1.1 tooth modules and in most cases greater than 1 25 tooth modules.
This reduced radius of curvature relative to that of involute profiles means that the gearing 15 disclosed herein is not geometrically conjugate in the transverse plane The gearing will therefore run most smoothly if the teeth are helical (or in the case of bevel gearing, spiral bevel) However, this «standard-pitch gearing» has a transverse (or «profile») contact ratio that when the gears are loaded is always larger than two and sometimes as large as six or seven, so spur or straight bevel teeth are quite feasible, particularly when the number of teeth 20 on the pinion is very large or the gear is internal.
Accordingly, the invention provides, in a pair of mating gears, teeth having working profiles of the transverse plane (as hereinafter defined) for which the radius of relative curvature (as hereinafter defined) at the pitch point is substantially smaller than the radius of relative curvature at the pitch point of a pair of meshing involute gears having the same pitch 25 circle diameters and pressure angle, but is greater than one and one- tenth tooth modules, the whole depth of the teeth (as hereinafter defined) or one of said pair of mating gears being greater than two and six-tenths tooth modules, the tooth pitch angle in the transverse plane for neither of said pair of mating gears being greater than 100.
According to the drawing the form of the working portion of the tooth profile is a circular 30 arc in the transverse plane However, since the teeth are quite fine, many curves that approximate a circular arc over a short segment are usable, including a segment of an ellipse such as is obtained in the transverse plane if the tooth profiles are circular arcs in the normal plane.
In addition to this reduced tooth profile radius of curvature, the teeth of gears embodying 35 the invention have a second distinguishing characteristic: They are much taller than conven- tional teeth Whereas standard 200 -involute teeth for power transmission gearing have whole depths of 2 4 to 2 6 tooth modules, those of the teeth embodying the invention range from at least two and six-tenths to values as high as 6 or more While this exceptional tooth depth has the advantage of increasing tooth flexibility and thereby making the gears less 40 susceptible to the deleterious effects of machining errors and misalignment, the main reason for the increased tooth depth is quite different: It is known (U S Patent No 3,824,373) that when gear teeth having a radius of relative curvature shorter than that of involute gears are lightly loaded, they make contact at a single point called a «culmination point» (U S Patent No 3937,098), but are separated by an amount that increases as the square of the distance 45 from the culmination point at other positions in their meshing cycle In gearing with relatively shallow teeth, nearly all of this separation is taken up by Hertzian deformation at the pitch point However, if the pinion has a large number of teeth, a very short radius of relative curvature is needed in order to control the bending stresses But values for the radius of relative curvature that are about half those of involute gears produce elliptical contact areas 50 having an eccentricity that is not appreciably affected by small changes in the tooth profile radii.
The purpose of the increased depth of the teeth is therefore to give the designer an additional parameter than can be used to offset the effects of the shortened radii in producing excessive lengthwise curvature of the teeth, so that any number of teeth may be specified for the pinion and it will still be possible to make the elliptical contact areas exactly fill the tooth working surface at a torque load that produces the maximum allowable stress at both the tooth root and the tooth contact surface How much extra depth the teeth must be given depends on the tooth module, tooth profile radii, addendum heights, the moduli of elasticity and the pressure angle Using these parameters in standard design and deformation analyses, 6 a however allows calculation of the particular dedendum depth that is required In all cases this depth will be found to be more than 1 6 tooth modules, or more generally, since the dedendum depths on the two gears may not be the same thesum of the dedendum depths for the two gears will be more than 3 2 tooth modules This means that at least one of the mating teeth will have a whole depth of more than two and six-tenths tooth modules If the gear has C an extra-long addendum the whole depth will usually be greater than two and three-quarters 3 1,568,898 3 wootn moaules.
In order to ensure that these exceptionally tall teeth have the lowest possible bending stresses at their roots in spite of their slender outline, the tooth flank thickness is increased continuously from the pitch circle all the way to the bottom of the tooth root These elongated flanks, for which profiles comprising parabolic or related exponential curves are well-suited, 5 do not carry any portion of the contact ellipses at any point in the meshing cycle, being utilized only to increase the tooth bending deflection The teeth of the external gears embodying the invention will thus have a working profile portion that is convex and an elongated flank portion that is usually concave and separated from the working profile portion by a point of inflection 20 10 It will be noted in the drawing that the line of action 21 makes a much smaller angle O a with the common tangent line 15 than the pressure angle 0 does This is because the line of action is generated by a point between arc centers T l and T 2 that is caused by the shortened radii r 1 and r 2 to move at a flatter angle a than the pressure angle 0 This leads to a large profile contact ratio, because the line 21 intersects the addendum circles (not shown) at points much 15 farther out from the pitch point P than those of an involute gear of pressure angle 0 It also means that only tooth profile portions lying beyond the line 21 can receive load, so the actual working profile is usually less than half the tooth whole depth especially in the case of the pinion 12.
The exceptional depth of the dedenda also means that the teeth embodying the invention 20 will nearly always have more clearance at the root than the value of 0 4 tooth modules that is most commonly specified in standard 20 ‘-involute gearing.
Although the type of gear tooth herein disclosed can be made with a wide variety of pressure angles, smaller pressure angles, not more than 200 and preferably less than 150, minimize operating noise, prevent the teeth from becoming pointed at the tips if an extended 25 addendum is used, and give a slightly higher torque capacity.
The third distinguishing characteristic of the gearing herein disclosed is that the pinion has an exceptionally large number of teeth Or expressed in terms of gear geometry that also applies to sectors of gears, the «tooth pitch angle» is exceptionally small (The term «pitch angle» as used in this specification means the angle in the transverse plane subtended at the 30 pinion central axis by corresponding points on adj acent teeth; for a full pinion it will therefore be 3600 divided by the number of teeth) The largest pitch angle that is practical in conjunction with the deepened dedendum is about 100, which puts 36 teeth on a full pinion This value would be for hardened steel or plastic gearing and the maximum recommended pitch angle for gears of unhardened steel is 35 close to 6 or 8 This means that for small gears the teeth may be so fine that tolerances on center-distance and pitch line runout may become difficult of impossible to meet Accord- ingly, the main area of application of «standard pitch gearing» is in gear sets where the pinion diameter is greater than about 15 millimeters, so that the number of teeth is in excess of the critical number of teeth for involute gearing of the same size, gear ratio and materials Since 40 the torque capacity does not decrease with tooth module as the gears become larger, it becomes feasible to standardize on a few modules that are fine enough to minimize noise, as well as friction, heating and wear, but coarse enough so that gears do not need to be down-rated to take account of errors in center-distances that result from standard machining and mounting techniques, that is to say, the anticipated manufacturing errors will not produce 45 a significant reduction in the interengagement depth of the teeth Standard tooth modules that meet both these requirements are in the range of 0 4 to 0 8 for vehicular and industrial gearing, and in the range of 0 8 to 1 3 for large marine gearing As these ranges are quite narrow, standardization on a single module in each range is quite feasible.
It will be noted that these values are from 3 to 20 times finer than the modules that would 50 ordinarily be specified for involute teeth for such applications As indicated, however, the use of these finer teeth does not reduce torque capacity, because the full load profile contact ratio increases as rapidly as the module decreases In fact, if the addendum heights for both gear and pinion are made greater than the conventional value of one tooth module, which is quite possible because of the extra dedendum depth, the torque capacity may be slightly larger than 55 that of a conventional involute gear set of the same size and materials.
A number of conventional modifications widely used with involute gears may also be applied to gearing of the type herein disclosed For example, the pinion and gear may be given unequal addenda by hob retraction or in-feed In the case of involute gearing, hob retraction 61 D is usually employed to prevent undercutting and tooth interference when the number of teeth 60 on the pinion is small In the case of «standard pitch» gearing, however, the purpose would be to increase the relative amount of recess action and to position the culmination point at the center of the line of action in large-ratio gear sets As in the case of involute gearing, profile-retraction or in-feed, which are also called negative or positive profile shift respec- tively, leads to differences in pinion and gear tooth thickness at the pitch circle In the case of 65 A 1,568,898 «standard pitch» gearing it also produces a slightly different pressure angle at the pitch circles.
As in the case of involute gears, the teeth may be crowned slightly in the lengthwise direction, either by grinding or by in-feeding of the hob at the tooth ends Because of the small size of the teeth, however, and their relative slenderness in the normal plane, a large amount 5 of crowning is not feasible This is not necessarily a disadvantage, however, since the teeth are so flexible that crowning will seldom be needed, and any additional relief considered necessary for alleviating tooth root bending stresses at the tooth ends can be provided more practically and economically by chamfering the ends of the teeth down to the pitch surface at about 450 Alternatively, the tooth ends at opposite faces of a set of gears may be chamfered 10 down to the point of inflection of the profile curve which marks the end of the working portion, using a chamfer angle that gives an effective face width of an integral number of axial pitch lengths at the culmination surface.
Although the drawing shows the pinion and gear teeth 11, 13 as being similar in shape, it is possible to make one profile quite short and to provide the necessary flexibility by making the 15 whole depth of the other tooth even greater than indicated in the figure This would alter the thickness of the teeth at the tooth roots but would have v ery little effect on the sum of the whole depths of the mating teeth needed to provide the required bending deflection at full load The sum of the whole depths for the mating teeth would still need to be at the very least five tooth modules, and preferably at least five and one-half tooth modules In addition, the 20 use of unequal tooth whole depths would double the required hob inventory.
It may be noted that the gear teeth herein disclosed are particularly adapted to fabrication from nitrided steel Since nitriding does not require a quench, it produces much less distortion than other forms of heat treating Its utility for involute gearing is limited by the fact that the case it produces is not as thick as the depth at which the most serious surface stress occurs in 25 larger gearing In «standard-pitch gearing», however, the shortened radius of relative curva- ture of the profiles brings this most severely stressed element sufficiently closer to the tooth surface to fall within a nitrided case.
Several points may be noted in connection with the tooling for manufacture of standard- pitch gearing: The point of inflection 20 of the tooth profile curves should be at a point where 30 the tangent to the profile makes an angle of at least 5 or 6 with a radial line This is about the smallest angle that will allow sufficient hob clearance for easy machining and will also allow the hob to be of the sharpenable ‘constant profile» type.
So far as hob inventory is concerned, the possibilities the subject invention affords to standardizing on a small number of gear tooth modules, as for example 0 5 to 0 8 should be 35 taken advantage of wherever possible Four or five hobs at each of these modules will be necessary for cutting different dedendum depths but an inventory of 10 or at most 15 hobs will be sufficient to cut all gears of all sizes In the involute system, on the other hand, the hob inventory needed for the same purpose may be two to three times as large, since hobs for involute pinions with small tooth numbers must usually be available in both right and 40 left-hand forms.
A number of design features that help to reduce noise emission may be used with the gearing herein disclosed For example, at least one of the mating pair (usually the larger gear) may be made of cast iron; a spoked web may be used in preference to a solid web; a layer or damping material such as plastic or rubber may be isnerted between the rim and web or one or 45 both gears or molded onto the end faces of one of both gears If one of the gears is made of cast iron and the other of steel, the latter should have a much greater dedendum depth than the former so that the cast iron gear will not be overstressed in bending.
It should be noted that the term ‘pitch circle» as used in gear specifications may be defined in two ways: 50 1 Any pair of gears is operable over a certain range of center-distances prescribed by the minimum and maximum interengagement the teeth will allow Changing the center-distance simply changes the tooth flank and tooth clearance, but the velocity ratio, which is governed by the number of teeth on each of the gears, is unaffected To take account of this center- distance variability, the «pitch circles» of a pair of gears are sometimes defined as those 55 circles that divide the center-distance in proportion to the velocity ratio, that is to say, the circles that have the same diameters as a pair of rollers that would afford the given velocity ratio when mounted at the given center-distance To avoid confusion, it is probably best to call these the «working pitch circles» and to bear in mind that the diameters of these «working pitch circles» vary somewhat depending on the particular center-distance used, and this in 60 turn produces minor variations in the pressure angle and addendum- dedendum proportions.
2 The «pitch circle» of a gear may also be defined in terms of the geometry of its teeth.
For example in the 20 -involute system, the «pitch circle» is most often construed as the circle that intersects the tooth profiles at a point where the tooth surface makes an angle of 20 with a radial line, and also divides the teeth into addendum and dedendum proportions 65 A 1,568,898 5 having heights prescribed by established standards (AGMA BS, DIN, etc) In effect, this second definition establishes theoretically correct or optimum center- distance and tooth clearance for the given gear type, as well as pressure angle and addendum- dedendum proportions (Note: This second definition should not be confused with «reference circle,» which concerns the radial displacement of a gear relative to the hob used to make it) In order that the tooth pressure angle and the addendum-dedendum proportions have specific values and shall not be subject to variations produced by extended or overly close center-distance mountings, the definition of «pitch circle» employed in this specification and the ensuing claims shall be construed as the second of these two definitions, rather than what o has been called above the «working pitch circle » 10 In this specification and the ensuing claims a number of other terms are employed that may require definition These are as follows: «Tooth flanks» means portion of the surface of the tooth that lies between the pitch circle as defined above, and the tooth root; «transverse» means lying in a plane perpendicular to the common pitch element (i e, the element common to the mating pitch surfaces); «pitch surface» means the cylindrical surface (or in the case of a 15 bevel gear, the conical surface) that contains the pitch circles of all transverse planes; «whole depth» means the sum of the addendum and the dedendum of a tooth, measured in a direction perpendicular to the pitch surface; «tooth» means a projecting portion of a gear body, and does not include a pin of the type used in lantern gearing; «dedendum» is the to portion of a tooth that lies between the pitch surface and the root surface, or if a slot is cut into 20 the root to increase the tooth flexibility, the portion of the gear that lies between the pitch surface and the portion of the slot farthest removed from the pitch surface; «dedendum depth» is the extent of the dedendum as herein defined, measured in a direction perpendicu- lar to the pitch surface; «critical stress» means the lowest stress that will produce permanent structural damage at any point in a tooth, comprising a yield point stress in a gear set 25 subjected to peak torque loads greater than twice the continuous operating torque, and a fatigue stress in all other gear sets; «culmination surface» means the surface of revolution that contains all culmination points; «addendum circle» means the locus of the point on the working profile of a gear tooth farthesr removed from the tooth root, when said gear turns about a fixed central axis; «working depth» means the maximum overlap distance between 30 the addendum circles of a pair of mating gear tooth profiles, measured perpendicularly to the gear pitch surfaces at their line of tengency; «line of action» means a line in the transverse plane that contains the locus of the center of the contact area intersection with said plane, which line in the case of the gearing herein disclosed lengthens or shortens depending on how much torque is being transmitted, but cannot extend beyond the points where it intersects the 35 addendum circles well outside the corresponding points for involute gears of the same size, gear ratio, tooth module, working depth and pressure angle.
WILLIAM S ROUVEROL Printed for Her Majesty’s Srataonery Office, by Croydon Printing Company Limited, Croydon Surrey 1980.
Published by The Patent Office, 25 Southampton Buildings London, WC 2 A LAY from which copies may be obtained.

GB48858/77A
1977-03-16
1977-11-23
Standardpitch gearing

Expired

GB1568898A
(en)

Applications Claiming Priority (1)

Application Number
Priority Date
Filing Date
Title

US05/778,260

US4108017A
(en)

1977-03-16
1977-03-16
Standard-pitch gearing

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Publication Date

GB1568898A
true

GB1568898A
(en)

1980-06-11

Family
ID=25112769
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Application Number
Title
Priority Date
Filing Date

GB48858/77A
Expired

GB1568898A
(en)

1977-03-16
1977-11-23
Standardpitch gearing

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US
(1)

US4108017A
(en)

JP
(1)

JPS53118654A
(en)

BE
(1)

BE861193A
(en)

GB
(1)

GB1568898A
(en)

IT
(1)

IT1090762B
(en)

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2017-05-03
2019-04-23
The Boeing Company
Self-aligning virtual elliptical drive

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The Boeing Company
Nutational braking systems and methods

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* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

US3937098A
(en)

1974-11-18
1976-02-10
Rouverol William S
High torque gearing

US4051492A
(en)

1976-01-13
1977-09-27
Polaroid Corporation
Photographic apparatus gear train having a unique set of gears

1977

1977-03-16
US
US05/778,260
patent/US4108017A/en
not_active
Expired – Lifetime

1977-11-23
GB
GB48858/77A
patent/GB1568898A/en
not_active
Expired

1977-11-25
BE
BE1008544A
patent/BE861193A/en
unknown

1977-11-30
IT
IT03626/77A
patent/IT1090762B/en
active

1977-12-02
JP
JP14561177A
patent/JPS53118654A/en
active
Pending

Also Published As

Publication number
Publication date

US4108017A
(en)

1978-08-22

IT1090762B
(en)

1985-06-26

JPS53118654A
(en)

1978-10-17

BE861193A
(en)

1978-03-16

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