USRE23728E - Automatic variable drive - Google Patents

Description

Oct. 27, 1953 M. TEIGMAN AUTOMATIC VARIABLE DRIVE Original Filed Feb. 15, 1946 FIG?) INVENTOR MAX TEIGMAN ATTORNEY Reissued Oct. 27, 1953 UNITED STATES Ti filTENT OFFICE Original No. 2,526,435, dated October 17, 1950,

Serial No. 647,793, February 15, 1946. Application for reissue August 18, 1951, Serial No.

14 Claims.

Matter enclosed in heavy brackets appears in the original patent but forms no part of this reissue specification; matter printed in italics indicates the additions made by reissue.

This invention relates to automatic variable drive.

An object of this invention is to provide a drive or transmission mechanism which is so arranged that the output speed increases automatically with increase in input speed, but in greater proportion to the increase of the input speed.

A further object of this invention is to provide a transmission or drive which is so arranged as to make it diificult for the input drive to be overloaded.

Still another object of this invention is to provide a transmission or drive which is so arranged that under load the output speed quickly decreases, thereby preventing the driving power from being overloaded. If a vehicle provided with a transmission mechanism embodying the invention climbs a hill or quickly passes another car on the road, the motor is prevented from being overloaded because the output slows down before the input is loaded. Then if the load is still heavy, the input slows down causing the output to further slow down but with a far greater proportion. The output, in accordance with the present invention, is so arranged as to slow down to a. greater degree than the slow down of the input so as to make it easier for the vehicle to climb a hill or to make it easy to pass another car on the road. Under no load for a given input speed its highest possible output is very quickly reached.

Still anotherobject of this invention is to provide an improved transmission of the character described which may be employed in conjunction with electric motors, gasoline motors, or any other rotary engines and maybe used in airplanes, buses, tractors, or for any rotary drive which involves a revolving input and a revolving output shaft. When used in conjunction with an electric motor my improved transmission will eliminate starting box because the electric currentneccssary to start is relatively low.

Yet another object of this invention is to provide an improved variable drive of the character described which shall be relatively inexpensive to manufacture, which shall have a variety of applications, and which shall be practical and efficient to ahigh degree in use.

"The invention accordingly consists in the features of construction, combinations of elements, and arrangement of parts which will be exemplifled in the construction hereinafter described, and of which the scope of application will 'be indicated in the following claims.

'In the accompanying drawing, in which is shown various possible illustrative embodiments of this invention,

Fig. 1 is a top plan view of a variable drive embodying the invention;

Fig. 2 is a .top plan view of variable drive embodying the invention and illustrating a'modified construction;

Fig. 3 is a top .plan view of a detail; and

Fig. 4 is a cross-sectional view taken on line 4-4 of Fig. 3[.]; and

Fig. 5 is a top plan view of a; variable drive emhedging the invention and illustrating another slightly modified construction.

Referring now in detail to the drawing, I I1 designates an automatic variable drive embodying the invention. The drive comprises a rotary, non-slidably mounted input shaft II which may be the output shaft of a vehicle motor or engine, and I2 designates an output shaft which may be connected by any suitable connection to a wheel of the vehicle.

Connected to the rotary shaft I I is a governor I3. Said governor I3 is connected to a shaft I4 coaxial with shaft II. On shaft II is a collar I5 provided with a plurality of apertured ears I Ii connected by links I! to governor weights I8. The governor Weights I8 are provided with apertured ears I9 .to which said links I I are connected. Said weights are also provided with apertured ears 2!) connected by links 2| to cars 22 ona collar 24 fixed to the shaft I4. The collar 24 is at one end of shaft I4. At the other end of shaft I4 is an annular friction disc .21. 'Theshaft I4 is slidably as well as rotatably supported in bearing 28.

Shaft II may be provided with an extension He. received in socket Ilb in shaft I4. The weights I8 are interconnected by tension spring I 8a, Slidably and rotatably supported in bearing 30 is a shaft 3| coaxial with shaft I4. On shaft 3I are a pair of oppositely extending pins 3Ib. 'Rotatably and slidably supported in beari-ng 30a is a shaft 3I'a coaxial with shaft II. On s'haft'3la is a collar -3Ic. Surrounding shaft 3Ia is a sleeve 31d biased to the right'looking at Fig. 1, bymeans of suitably anchored tension springs 31c. Shaft illa is formed with a socket 3If rotatably and slidably receiving the adjacent end of shaft 3 I. Thesocket 3 If is formed with a pair of oppositecammed slots 31g through which the pins -3Ib project. Shaft 31 is interconnected to shaft Me. by coil, tension spring 3th disposed within the socket.- on shaft -3-Ia is asecond collar 3 ll adapted to contact-a suitable annular-stop 3 If] surrounding shaft 3I a. It will now'be-understood that the sleeve 3|d may engage the collar 3 c and will move shaft 3 la to the right until collar 3 ii contacts the stop 3 Li.

Fixed on shaft 3|a for rotation therewith is a friction wheel 32. At one end of shaft 3| is a circular cage 34, surrounding disc 21 and having an inturned annular lip or flange engaging the inner side of said disc.

It will now be understood that when the output shaft speeds up, the weights l8 will fl out and draw shaft It to the left. Disc 21 will contact the flange or lip 35 of cage 34 and hence draw shaft 3| to the left. The disc 21 is a friction disc and frictionally engages the annular flange or lip 35 so that shaft 3| will rotate to gether with shaft M. As shaft 3| is drawn to the left, the friction wheel 32 will likewise be drawn to the left for the purpose hereinafter appearing.

For the purpose hereinafter appearing, there is rotatably mounted on an axis inclined to the axis of shaft 3|, a shaft 4|). Shaft is rotatably supported on a pair of spaced bearings 4|. Interposed between the bearings 4| and fixed abutments 32 are coil compression springs 43 which serve to press shaft 4|] towards shaft 3|. ihe shaft 43 is non-slidably mounted on the bearings 3|. On shaft 40 is a friction cone [43] 44 adapted to contact the friction wheel 32. In fact the springs 43 press the friction cone is against the friction wheel 32. On shaft 43, and between the bearings, is a bevel gear 15, for the purpose hereinafter appearing.

Rotatably and non-slidably mounted on suitable bearings 53 is the output shaft l2, which is coaxial with shaft Ii. On said output shaft is a gear 5| meshing with the bevel gear 45. It will be noted that shaft I2 is coaxial with shafts H, M and 3|. When the shaft II is stationary, the friction wheel 32 is substantially at the high or right end of cone 4 It will be noted that the cone is tangent to a plane parallel to the axis of shaft 3| so that as the speed of shaft increases and the governor weights fly out, shaft 3| will be pulled to the left, but the friction wheel 32 will remain in contact with the cone M.

It will now be understood that the transmission is through shaft ll, governor l3, shaft l4, coupling Slf, shaft 3|, shaft 3| a, friction wheel 32, friction cone M, gears and 5| to output shaft l2. shaft IE will rotate at a low speed and the output speed will increase at an accelerated speed as the input speed increases. Little poweris required to start rotation of the output shaft because it starts at very low speed. Under load the increase in speed is more gradual because coupling 3|f under such conditions decreases speed of output shaft l2 in addition to the fact that when the input drive is loaded the governor would still further decrease output speed at a (slowing up) rate of speed. In case of a hill when the motor connected to'shaft is overloaded and slows down, shaft i2 will slow down still further to permit the vehicle to more easily climb the hill and thereby using the full power of the motor. When travelling on level roads, the speed increases with acceleration quickly, still using substantially full load.

When riding a level road, the car is geared almost to its highest capacity for a particular input speed. When coasting, it is geared to its fullest capacity for that speed. When accelerating or going up-hill the car goes into lower gear (as explained before) which makes thecar accelerate without overloading the motor.

As shaft begins to turn, the output The gear 7 range quickly goes back to its high for that speed, automatically, when no load is encountered. The clutch 21, 35 could be adjusted to disengage only when idling at very low speed. If the governor spring |8a is stronger than the pull springs 3ie, shaft M will move more quickly than shaft 3| causing the free Wheeling when the drive (accelerator pedal) is released. If the pull springs 3 le are stronger than the governor springs, shaft 3| will move back faster than shaft i=1, thereby keeping the friction clutch 21, 35 engaged until the stop is reached. Then the clutch will disengage upon the drive slowing down. The stop 3|j can be so adjusted or located that the clutch will disengage at idling speeds.

It will further be understood that when the shaft 3| is rotating at low or normal speeds, the pins 3lb will remain as shown in the drawing. However, should the drive encounter a big load, the pins 3lb will slide in the cam slots 3 lg thereby moving shaft 3|a to the right, looking at Fig. 1, and putting the gearing into a lower register. When such action occurs, the spring 3|h is tensioned and tends to bring the shaft 3|a back to normal longitudinal position when the load decreases. It will therefore be understood that normally, the shafts 3| and 3|a rotate together but in case of load there is relative rotation between said shafts as well as relative sliding movement to change the gear register.

If desired the governor can be eliminated and a manual clutch substituted for clutch 21, 34, 35. In such event the length of slots 3|g could be substantially the same length as cone 44, and the wheel 32 would be at the small end of the cone when not turning. The starting load would then move wheel 32 toward the large end of the cone to start the output shaft at lower speed. Before the output shaft starts to turn, the wheel 32 moves to a point where it can start rotating the cone and hence the output shaft.

If desired the governor can be adjusted for just enough movement to actuate the clutch 21, 34, 35, and in such case the coupling 3|f would be of the length of the cone and operate as described above.

Furthermore if desired coupling 3if may be eliminated, see Fig. 5, so that the governor will move the wheel 32 the length of cone 4%.

Flexible shafts or desirable gearing could be interposed in [slots] shafts 14 or 3| to arrange the output shaft at any desirable angle relative to the input shaft.

In Fig. 2 there is shown a transmission or variable drive Hia, embodying the invention, and illustrating a modified construction. In Fig. 2 [I [la] 63 designates an input shaft which may be connected to the motor of a vehicle, and BI indicates the output shaft which may be connected by suitable gearing to the wheels of the vehicle.

Slidably mounted in any suitable support (not shown) is a yoke 62 having parallel arms 63 and 33. Arm 33 is provided with a bearing 55. Rotatably mounted in the bearing 35 is a shaft 66. Shaft 63 is non-slidable relative to bearing 65. Shaft 66 is furthermore provided with an integral sleeve 61 formed with an opening or socket 68 coaxial with shaft 60. Fixed to shaft 3|] is an extension 69 slidably engaged within the opening 68. Interconnecting shafts 60 and 66 is a speed governor 10. Said governor comprises a collar 1| fixed to shaft 69 and provided with apertured ears 12. Pivoted tothe cars 12 are links 13. The governor further comprises a plurality of weights 14 each provided with a pair same of ears 15 and 16'. Links 13 connect the ears 12 with the ears 15. On sleeve 61 are ears 11 connected by links 18 to the cars 16. The shaftffl is non-slid'ably mounted in any suitable bearings. Itwill now be understood that as" the shaft 60* increases in speed, the weights T4 will fly out; thereby causing shaft 66. to slide to the left'asxit rotates. Such movement of shaft 66 will pullthe yoke 52 to the-left therewith. On; shaft 66. and. disposed within the yoke" is a gear 85. Arm 64 is parallel to. arm 63. and is provided with ,alongitudinal slot 81. Slidably mountediwithin the slot is a bearing 82.. Extending through the bearing 824s a shaft83. On shaft: 83 is aigeartl mesh.- ing, with gear 80. The bearing 82 is. provided with collars 86' engaging opposite-sides of yoke arm 64.. Shaft 83 is non-slidably' connected to hearing 82'. It will now be understood that as the yoke 62 is pulled. to the. left, it will also. pull shaft 83 to the'left as said shaft rotates. On shaft. 83 is a small friction cone 8]. On the output shaft 5! is a large cone 85, frictionally engaging the cone 81. It will'benoted thatthe cones 8'! and 85 point in opposite directions;

On shaft 83 is a sleeve 90 connected'by coil compression spring 9! to a fixed anchor 92'. Spring 91: tends to press the cone 8! against the cone 85. It will now be understood that as the speed of shaft 64! increases, shaft 66 will be pulled to the left, pulling yoke 62 to the left therewith. Such movement of the yoke 62 will carry shaft 83 to the left and move cone 8'! down to the small and of the large cone 85 thereby increasing the speed of the output shaft progressively. Shaft 83 may tilt due to the sliding. connection: of bearing 82 in the slotted arm 64.

It will be understood'that the cones 81, 85 may be replaced byfriction discs at right angles to each other so that the shaft 61 will be at right angles to the shaft B3.

In Fig. 5 there is shown a modified construction of the invention which is exactly the same ras the device shown in Fig. 1, with the exception that the coupling 31 f is eliminated, and shaft 31a is aicontinaation of shaft 31.

It will thus be seen that there is provided a device in which the several objects of this invention are achieved. and which. is well adapted to meet the conditions of practical use.

As variouspossible embodi'mentsmight be made of the above invention, and as various changes might be made in the embodiments above set forth, it is to be understood that all matter herein set forth or shown in the accompanying drawing is to be interpreted as illustrative and not in a limiting sense.

Having thus described my invention, I claim as new and desire to secure by Letters Patent:

1.. In combination, a non-slidable, rotary shaft, a rotary and slidable shaft, a governorv connecting. said shafts, a second rotary and slidable shaft, friction means to interconnect said rotary and slidable shafts, means to limit movement of said second rotary and slidable shaft in one direction, a friction wheel on the second rotary and slidable shaft, a rotary friction cone contacting said friction wheel, an output shaft, and gearing connecting said output shaft with said friction cone.

2. In combination, a non-slidable, rotary shaft, a rotary and slidable shaft, a governor connecting said shafts, a second rotary and slidable shaft, friction means to interconnect said rotary and slidable shafts, means to limit movement of said second rotary and slidable shaft in one direction, a friction wheel on the second rotary and slidslidable shaft. in one. direction, a friction, drive member onthetsecond rotary and slidable shaft,

and a friction conein. contact with said friction and drive member..

4. Aninput rotary shaft, a. rotary and slidable shaft coaxial. therewith, a governor interconnect.- ing said shafts, a second rotary and slidable shaft, means to connectsaid rotary and. slidable shafts for rotation and sliding movement, means to limit movement of said second rotary and slidables shaft in one direction, a friction drive memher on the second rotary and slidable shaft, a friction cone: in: contact with said friction and. drive member, and spring means to maintain the friction drive member and friction cone in frictional contact.

5. A drive comprising an input rotary and nonslidable shaft, a rotary and slidable shaft, a speed governor interconnectingscid first two shafts, a second slidable and rotary shaft, a friction clutch interconnecting said rotary and slidable shafts, a third rotary and slidable shaft, means connecting said second and third: rotary and slidable shafts to" permit relative rotation and sliding movement therebetween, spring means interconnecting said second and third slidable and rotary shafts, a friction wheel on said third. rotary and slidable-shaft; and a friction cone engaging said. frictionvwheel, and means to limit movement of said thirdrotaryrand slidable shaft inone directiorn 6. A. drivecomprising an input rotary and horn slidable. shaft, a rotary and slidable shaft, a speed governor interconnecting said first two shafts, a second slidable and rotary shaft, a friction clutch interconnecting said. rotary and. slidable shafts; athirdrotary' and slidable shaft, means connect,- ing said second and. third. rotary and slidable shafts to permit-- relative rotation and sliding movement therebetweem. a friction wheel on said third rotaryandi slidable shaft, a friction. cone engaging said friction wheel, spring means interconnecting saidsecond and third slidable and rotary shafts, and spring means tending to move said third slidable and rotary shaft in one direction and means to limit movement of said third rotary andsli'dable shaft in one direction.

7. In combination, a non-slidable, rotary shaft, a rotary andsli'da-ble shaft, a governor connecting said shafts, a second rotary and slidable shaft, clutch means to interconnect said rotary and slidableshafts, means to limitmovement of said second rotary and slidable shaft'in one direction, a friction wheel on the second slidable and rotary shaft, a .rotary friction cone, contacting said friction Wheel, an output shaft, and gearing connecting said output shaft with said friction cone.

8. In combination, a non-slidable, rotary shaft, a rotary and slidable shaft, a governor connecting said shafts, a second rotary and slidable shaft, clutch means to interconnect said rotary and slidable shafts, means to limit movement of said second rotary and slidable shaft in one direction, a friction Wheel on the second slidable and rotary shaft, a rotary friction cone contacting said friction wheel, an output shaft, and gearing connecting said output shaft with said friction cone, and spring means to press said friction cone against said friction wheel.

9. A drive comprising an input rotary and non-s1idab1e shaft, a rotary and slidable shaft, a speed governor interconnecting said first two shafts, a second slidable and rotary shaft, a I

clutch means interconnecting said rotary and slidable shafts, a third rotary and slidable shaft, means connecting said second and third rotary and slidable shafts to permit relative rotation and sliding movement therebetween, spring means connecting said second and third slidable and rotary shafts, a friction wheel on said third rotary and slidable shaft, a friction cone engaging said friction Wheel and means to limit movement of said third rotary and slidable shaft in one direction.

10. In combination, a rotary shaft, a slidable and rotary shaft, a torque sensitive coupling interconnecting said two shafts with the degree of sliding movement of the slidable and rotary shaft being dependent upon the torque imposed on the latter, an output shaft, and a variable speed transmission interconnecting the slidcble and rotary shaft with said output shaft, with the speed of said output shaft being dependent upon the degree of sliding movement of said rotary and slidable shaft.

11. In combination, a rotary and non-slidable input shaft, a slidable and rotary shaft, means including a speed governor interconnecting said two shafts, with the degree of sliding movement of the slidable and rotary shaft being dependent upon the speed of the input shaft, fired diameter means on said slidable and rotary shaft rotating therewith, an output shaft, and variable speed transmission interconnecting the fixed diameter means with the output shaft, with the speed of the output shaft dependent upon the degree of sliding movement of said slidable and rotary shaft.

12. In combination, a non-slidable and rotary input shaft, a slidable and rotary shaft, a speed governor interconnecting said shafts, with the degree of sliding movement of said slidable and rotary shaft being dependent upon the speed of the input shaft, a second slidable and rotary shaft, means including a torque sensitive coupling interconnecting said first and second slidable and rotary shafts, with the degree of sliding movement of said second slidable and rotary shaft relative to the first slidable and rotary shaft being dependent upon the torque imposed on said second slidable and rotary shaft, an output shaft, and avariable speed transmission intereonnecting said second slidable and rotary a shaft with said output shaft, with the speed of the output shaft being dependent upon the degree of sliding movement of the second slidable and rotary shaft.

.13. In combination, a non-slidable and rotary input shaft, a slidable and rotary shaft, a speed governor interconnecting said two shafts, with the degree of sliding movement of said slidable and rotary shaft being dependent upon the speed of the input shaft, a second slidable and rotary shaft, a clutch interconnecting said first and second slidable and rotary shafts for rotary and sliding movement together therewith, a third slidable and rotary shaft, a torque sensitive coupling interconnecting said second and third slidable and rotary shafts, with the degree of sliding movement of the third slidable and rotary shaft relative to the second slidable and rotary shaft being dependent upon the degree of torque imposed upon said third slidablc and rotary shaft, an output shaft, and a, variable speed transmission interconnecting said output shaft with the third slidable and rotary shaft, with the speed of the output shaft being dependent upon the degree of sliding movement of said third slidable and rotary shaft.

.14. In combination, a rotary shaft, a slidable and rotary shaft, a torque sensitive coupling interconnecting said two shafts with the degree of sliding movement of the slidable and rotary shaft being dependent upon the torque imposed on the latter, an output shaft, and a variable speed transmission interconnecting the slidable and rotary shaft with said output shaft, with the speed of said output shaft being dependent upon the degree of sliding movement of said rotary d d le f said coupled shafts being coaxial and said coupling comprising spring tension means urging movement of said shafts toward each other, and means to permit relative rotation between said coupled shafts.

MAX TEIGMAN.

References Cited in the file of "this patent or the original patenlt UNITED STATES PATENTS Number Name Date 821,631 Felt May 29, 1906 863,434 Pattison et a1 Aug. 13, 1907 1,137,507 McKeever Apr. 27, 1915 1,246,683 Tooth Nov. 13, 1917 1,428,326 Fay Sept. 5, 1922 1,587,645 Hicguct June 8, 1926 1,650,594 Bing Nov. 29, 1927 1,772,593 Robertson Aug. 12, 1930 1,781,761 Mayer Nov. 18, 1930 1,837,978 McGavern et a1. Dec. 22, 1931 2,243,321 Smith May 27, 1941 FOREIGN PATENTS iumoer Country Date 321,231 Great Britain Nov. 7, 1929 436,705 Germany Nov. 6, 1926 600,149 France Nov. 3, 1925 798,244 France Mar. 2, 1936

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