US3097538A - Gubbiotti - Google Patents

Gubbiotti Download PDF

Info

Publication number
US3097538A
US3097538A US3097538DA US3097538A US 3097538 A US3097538 A US 3097538A US 3097538D A US3097538D A US 3097538DA US 3097538 A US3097538 A US 3097538A
Authority
US
United States
Prior art keywords
sleeve
output shaft
drum
bore
shaft
Prior art date
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 - Lifetime
Application number
Other languages
English (en)
Priority date (The priority date 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 date listed.)
Publication date
Application granted granted Critical
Publication of US3097538A publication Critical patent/US3097538A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
    • F16H29/04—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts
    • F16H29/06—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts with concentric shafts, an annular intermediate member moving around and being supported on an adjustable crank or eccentric
    • 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
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • 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
    • Y10T74/15—Intermittent grip type mechanical movement
    • Y10T74/1503—Rotary to intermittent unidirectional motion

Definitions

  • the purpose of this invention is to provide a continuous speed variator the operation of which is exclusively mechanical, in order to obtain an etliciency far higher than that obtainable by hydraulic variators.
  • Another purpose of this invention is to provide a variator of the cited kind, suitable to be mounted either on industrial machines or to be used with the drive of vehicles.
  • the variator according to this invention makes it possible to dispense with the friction clutch and the differential.
  • a unit comprising, in combination, an input shaft to which the motive power is applied, a cylindrical drum rigid with said shaft and internally provided with a circular cross-section eccentric recess, a sleeve received in the recess, and also provided with an eccentric recess the eccentricity of which is equal to that of the cylindrical, a further sleeve having an annular cross-section mounted in said cylindrical recess of said first-mentioned sleeve, an output shaft received in said further sleeve, andprovided with cross-seatings, means allowing said further sleeve to make translational movements, but preventing said sleeve from rotating about its axis, thrust elements mounted in said seatings to transmit the movement of said annular cross-section sleeve to the output shaft, and means for changing at will the relative position of the two eccentric recess cylinders and therefore the drive ratio.
  • FIG. 1 is a side view of the variator partially in cross section and taken along a vertical plane;
  • FIG. 2 is a cross-sectional view taken along the plane II-II of FIG. 1;
  • FIG. 3 is a cross-sectional view taken along the plane TIL-III of FIG. 1;
  • FIG. 4 is a partial cross-sectional view taken along the line IVIV of FIG. i1;
  • FIG. 5 is a cross-sectional View taken along the plane V-V of FIG. 4;
  • FIG. 6 is a cross-sectional view taken along the plane VIVI of FIG. 3;
  • FIG. 7 is a side view of the output shaft, partially in cross-section and taken along an axial longitudinal plane;
  • FIGS. 7A, 7B, 7C, 7D, 7E show, in the cited order, the cross-sectional views corresponding to the planes A-A, BB, C-C, D-D and EE, respectively;
  • FIG. 8 shows the detail, on an enlarged scale, one of the thrust elements
  • FIG. 9 is a side View of the detail of FIG. 8, and
  • FIG. 10' is a cross-sectional view taken along the plane XX of FIG. 9.
  • the input shaft 1 is connected to a prime mover of any type, not shown.
  • the shaft 1 is journaled in a roller bearing 2 supported by a case 3 provided with a bed plate 4, and terminates in a flange 5 to which, by means of a set of screws 6, is fixed a first cylindrical drum 7 internally provided with a circular cross-section eccentric bore 8.
  • a second cylindrical drum 9 which is also provided with an internal eccentric bore 10 into which a tubular sleeve 11 is inserted.
  • the drum 9 and the sleeve 11 are immersed in an oil bath, the oil for which is fed into the drum 7 through an aperture closed by means of the screw 16.
  • the front portion of the drum 7 is connected to the collar 12 which in turn is rotatably mounted on the hollow hub 14 by means of the roller bearing 13. Between said two elements a seal ring .15 is inserted having the function of preventing the lubricating oil from escaping.
  • the hollow hub 14, in turn is fixed rigidly by a lock screw 17 to a cap 18 which is fastened to the case '3 by the bolts 19.
  • a roller bearing 21 is mounted between the hollow hub 14 and the cap 18, and said roller bearing, in the conditions shown in FIG. 1 is inoperative because of the lock screw 17 fixing the hub 14 rigid with the case 3, as aforesaid.
  • the tubular sleeve 11 is fixed by the screws 21 to a bushing 22 forming part of a double slider coupling (shown also in FIGS. 4 and 5) which bushing is provided with two front dogs 23 on diametrically opposite sides of the axis of sleeve 11.
  • Two other front dogs 24 on the opposite ends of a diameter at to the alignment of dogs 23 are carried by the hollow hub 14 forming a second part of the coupling (FIG. 5).
  • Said pairs of front dogs enter corresponding notches 25 of a ring 26, which forms the third part of the coupling, and having the function of preventing the tubular sleeve 11 from rotating about its axis, although allowing a limited transverse translation movement of said sleeve.
  • the output shaft Concentrically with the hub 14 (FIG. 1) is mounted the output shaft generally denoted at 2.7 to which the resistant torque is applied.
  • the output shaft 27 is supported by the pair of ball bearings 28 spaced apart by the spacer 29, and by the bearing 30 mounted at the inner end of the shaft, near the flange 5.
  • a set of transverse seats 31 (FIGS. 7 to 7E) parallel to one another is provided in the shaft 27 and said seats are equiangularly spaced around the output shaft. In the illustrated example, there are five seats 3-1 angularly spaced from each other by 72.
  • a thrust element In each transverse seat 31 is positioned a thrust element generally denoted at 32, said thrust element being shown in detail in FIGS. 8 to 10.
  • Each element 32 has a length slightly less than the diameter of the inner periphery 33 of the tubular sleeve 11 and the ends of said element 32 are shaped to match the contour of the inner periphery 3 3.
  • the body 32 of the thrust element is provided with an inner groove 34 wherein is received a set of rollers 35 on which rests a sliding block 36 slidable between two end abutments 37 and 38.
  • the sliding block 36 is provided with a little notch 39 in which rests the tooth 46 on the corresponding seat of the shaft 27.
  • each seat 31 On the opposed sides of each seat 31 is provided a periph eral groove 41 and in each groove 41 is positioned a helical spring 42.
  • Each pair of springs 42 is fastened at one of its ends to a cross-member 43, while the other end carries a pin 44 resting against the rear surface of the thrust element 32 urging the sliding block 36 against the corner 40.
  • a vertical projection 45 is provided in the upper portion of the case 3, and in said projection is positioned a stem 46 carrying a hand wheel 47 and connected by a knuckle 48 to a threaded bolt 49 (FIGS. 1 and 2).
  • the latter is threaded into a nut 50 connected by the stud 51 to a fork 52 carried by the rocking lever 53 the pivot pin 54 of which is capable of sliding in an elongated hole 55 in a member 55a mounted in projection 45.
  • the lower end of the lever 53 is provided with another fork 56 the ends of which are connected by the pins 57 to the bushing 58 mounted on the bearing 5i
  • the latter is mounted on the collar 60 which is provided with the plain bearing 61 through which passes the shaft 1.
  • the collar 60 is bodily connected to the yoke 62 (FIG. 6) at the ends of which are mounted the two pins 63 slidable in seats 64 provided in the drum 7.
  • the pins 63 terminate in two oblique teeth 65 which are engaged in helical guide grooves 66 provided on the outer periphery of the drum 9.
  • the device operates as follows:
  • the pins 63 slide in the seats 64 provided in the drum 7, and their teeth 65, guided in the grooves 66, rotate the drum 9 with respect to the drum 7 which, being directly coupled to the shaft 1, rotates with the latter.
  • the operation of the hand wheel 47 has the effect of changing the relative position of the drums 7 and 9 which simultaneously rotate, driven by the shaft 1, to which the driving torque is applied.
  • the drums 7 and 9 are provided with inner recesses the eccentricities of which are equal, whereby when the positions of the drums is that shown in FIG. 3, the two eccentricities compensate for each other, and the tubular sleeve 11 is thereby perfectly centered and does not rotate about its axis being held by the ring 26. Under these conditions, the output shaft 27 is stationary.
  • the inner circular bore of the drum 9 takes an eccentric position whereby the sleeve 11, driven by the unit of the drums 7 and 9, always with no rotational movement about its axis, moves along a circular translation path, with a radius corresponding to the diiference in eccentricity between the drums 7 and 9.
  • the movement of the sleeve .11 causes its axis (to move along a circular path. Assuming that this movement occurs clockwise starting from the position shown in FIG. 7A, a thrust action of the thrust element 32 occurs against the corner 40 of the output shaft 27.
  • the tangential component generated by said action is converted into a sliding movement of the sliding block 36 while the component at right angles to the sliding block 36 causes a rotation of the output shaft 27 through an angular distance corresponding to the stage of active thrust of the considered element, said stage being 72.
  • the subsequent thrust element FIG.
  • the thrust elements 3 2 When the thrust elements 3 2 are out of their active stage, i.e. are not pressed against the corner 40, the continuity of the contact between the sliding block 36 and the corner 40 is ensured by the springs 42, as aforesaid. Under these conditions, the thrust elements rotate with a slight frictional sliding movement on the inner surface of the sleeve 11.
  • a mechanically operating continuous speed variator with an input shaft adapted to be connected to a prime mover and having a first cylindrical drum fixed to said shaft and having an internal circular eccentric bore and two opposed longitudinal recesses at the front end thereof, a second drum positioned in said bore and also having a circular eccentric bore with an eccentricity equal to that of said first drum and having helical guide means on its outer surface, a unit comprising in combination an annular sleeve mounted in the bore of said second drum, a collar fixed on said sleeve, an output shaft aligned with said sleeve, a tooth on said output shaft, a hollow hub carrying said output shaft, a double slider coupling connecting said sleeve to said hollow hub and allowing translational movements of said sleeve, hindering rotational movement thereof about its axis, said output shaft having recessed transverse seats therein, a thrust element mounted in each of said transverse seats for transmitting the movement of said annular sleeve to said output shaft, said thrust elements each having
  • said thrust elements are bars extending crosswise with respect to said sleeve and mounted within said recesses for the transverse seats in said output shaft, said bars being parallel to one another and equiangularly spaced a distance equal to 360 divided by the number of said bars, said thrust elements converting a circular translational movement of said sleeve into a rotational movement of said output shaft and acting sequentially thereon.
  • said double slider coupling consists of a ring concentrical with said output shaft and having two pairs of notches located on lines at right angles, and two pairs of front dogs, one pair engaging in each groove, one pair of front dogs being on said hollow hub and the other pair on said collar.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
  • Transmission Devices (AREA)
US3097538D 1960-01-11 Gubbiotti Expired - Lifetime US3097538A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT30160 1960-01-11

Publications (1)

Publication Number Publication Date
US3097538A true US3097538A (en) 1963-07-16

Family

ID=11098495

Family Applications (1)

Application Number Title Priority Date Filing Date
US3097538D Expired - Lifetime US3097538A (en) 1960-01-11 Gubbiotti

Country Status (5)

Country Link
US (1) US3097538A (en))
BE (1) BE597768A (en))
CH (1) CH376335A (en))
GB (1) GB966105A (en))
NL (2) NL126157C (en))

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US637477A (en) * 1899-07-03 1899-11-21 William Henry Newman Variable-speed gear.
US692077A (en) * 1901-07-09 1902-01-28 Archibald Sharp Continuously-variable-speed gear.
US703629A (en) * 1901-04-06 1902-07-01 Louis T Weiss Variable-speed gearing.
US787830A (en) * 1904-10-18 1905-04-18 William C Conant Variable-speed gearing.
US1079044A (en) * 1912-09-25 1913-11-18 Thomas Foster Variable gear.
US1343254A (en) * 1920-06-15 Gearless variable-speed transmission
US1470564A (en) * 1913-11-08 1923-10-09 Hall Co Transmission mechanism
US1872636A (en) * 1931-01-17 1932-08-16 Galloway Engineering Company L Variable speed transmission
US2364393A (en) * 1943-08-18 1944-12-05 Ferdinand W Seeck Gearless variable speed transmission
US2677968A (en) * 1951-04-03 1954-05-11 Hubner Kamill Speed changing mechanism

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1343254A (en) * 1920-06-15 Gearless variable-speed transmission
US637477A (en) * 1899-07-03 1899-11-21 William Henry Newman Variable-speed gear.
US703629A (en) * 1901-04-06 1902-07-01 Louis T Weiss Variable-speed gearing.
US692077A (en) * 1901-07-09 1902-01-28 Archibald Sharp Continuously-variable-speed gear.
US787830A (en) * 1904-10-18 1905-04-18 William C Conant Variable-speed gearing.
US1079044A (en) * 1912-09-25 1913-11-18 Thomas Foster Variable gear.
US1470564A (en) * 1913-11-08 1923-10-09 Hall Co Transmission mechanism
US1872636A (en) * 1931-01-17 1932-08-16 Galloway Engineering Company L Variable speed transmission
US2364393A (en) * 1943-08-18 1944-12-05 Ferdinand W Seeck Gearless variable speed transmission
US2677968A (en) * 1951-04-03 1954-05-11 Hubner Kamill Speed changing mechanism

Also Published As

Publication number Publication date
BE597768A (fr) 1961-03-31
NL258607A (en))
GB966105A (en) 1964-08-06
CH376335A (it) 1964-03-31
NL126157C (en))

Similar Documents

Publication Publication Date Title
US3013447A (en) Eccentric drive transmission mechanism
US1903228A (en) Frictional gearing
US2325502A (en) Speed varying device
US3874253A (en) Waddington drive
EP0557369B1 (en) Toroidal race rolling-traction type transmission
RU2382917C2 (ru) Устройство бесступенчатого регулирования передаточного отношения (вариатор)
US3097538A (en) Gubbiotti
US3728912A (en) Bicycle transmission
US2973653A (en) Infinitely variable gear
US2108082A (en) Transmission mechanism
US2939343A (en) Power load equalizer
US2123007A (en) Tractive pressure means for frictional power transmission mechanisms
US2178784A (en) Variable speed transmission
US1821833A (en) Variable speed power transmission mechanism
GB1167342A (en) Improvements relating to Variable-Ratio Frictional Drives
US1816295A (en) Speed changing gear and clutch therefor
US2346752A (en) Transmission gearing
US3138960A (en) Infinitely variable speed transmission and differential drive therefor
US3656356A (en) Continuous gear-type speed variator
US2455842A (en) Power transmission mechanism
US2223711A (en) Variable speed mechanism
US2350627A (en) Clutch mechanism
US1832384A (en) Variable speed transmission mechanism
US561260A (en) Johannes gkimhe
US2434590A (en) Hydraulic transmission