US3227004A - Torque converter - Google Patents

Torque converter Download PDF

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Publication number
US3227004A
US3227004A US263163A US26316363A US3227004A US 3227004 A US3227004 A US 3227004A US 263163 A US263163 A US 263163A US 26316363 A US26316363 A US 26316363A US 3227004 A US3227004 A US 3227004A
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Prior art keywords
shaft
ring
ring member
revolution
rotation
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US263163A
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English (en)
Inventor
Orain Michel
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Glaenzer Spicer SA
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Glaenzer Spicer SA
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    • 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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
    • F16H15/50—Gearings providing a continuous range of gear ratios
    • F16H15/52—Gearings providing a continuous range of gear ratios in which a member of uniform effective diameter mounted on a shaft may co-operate with different parts of another member
    • 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
    • F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
    • F16H13/06—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion
    • 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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
    • 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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
    • F16H15/50—Gearings providing a continuous range of gear ratios
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S475/00—Planetary gear transmission systems or components
    • Y10S475/904—Particular mathematical equation

Definitions

  • An object of the invention is to obtain a torque converter that is highly efficient.
  • Another object of the invention is such a torque converter in which the speed of the output shaft can be varried from zero to direct transmission with the input shaft by automatic or manual control
  • a further object of the invention is a torque converter in which the direction of rotation of the output shaft can be reversed.
  • the invention which is connected between a motor and a machine, greatly simplifies or entirely replaces the starting up means of the machine.
  • the torque converter of the invention essentially comprises a driving ring, or driver, rotatively coupled to the input shaft of the converter; a driven ring rotatively coupled to the output shaft; and a reaction ring, or reactor, rotatively coupled to the converter housing and absorbing the difference between the torque applied to the input shaft and the out-put shaft.
  • the three rings are substantially coaxial and each is in tangential contact with its neighbour, there being altogether two points of contact, under the action of centrifugal force.
  • the rings can have internal or external treads that are surfaces of revolution, with straight or curved generatrices.
  • the tangential contact can be inside or outside or both.
  • the rings can have support surfaces that have double tapers or conicities, .to permit reversal of direction of the output shaft with respect to the input shaft.
  • the coupling between the drive and driven rings and the input and output shafts, respectively, consists of universal joints or equivalent means.
  • the center of gravity can be kept substantially still by placing adjustable elastic means between, preferably, the reaction ring and the converter housing.
  • the converter can comprise doubled drive and driven members, each member being shifted 180 in the plane of rotation from its other member, whereby the reactor receives only balanced forces, and the two members, whether driven or driving, being coupled by an Oldham joint or other equivalent joint.
  • FIG. 1 is a view in section of one embodiment of the rings
  • FIG. 2 is an end of the embodiment of FIG. 1;
  • FIGS. 3, 4, and 5 schematically show how the torque is transmitted from one ring to another
  • FIG. 8 shows means for facilitating the starting-up of the conical rotation of the transmitter
  • FIG. 9 shows an arrangement for reversing the direction of rotation of the output shaft with respect to that of the input shaft
  • FIG. 10 shows a system of weights acting on the driven ring
  • FIGS. 11 to 24 schematically show various arrangements of the rings.
  • the converter of the invention essentially comprises three elements of revolution: a driving ring 1 rotatively coupled to the input shaft of the converter; a driven ring 2 rotatively coupled to the output shaft; and a reaction ring 3 fixed to the housing of the converter.
  • the rings 1 and 2 are indicated as in mutual contact at point A and rings 2 and 3 at point B.
  • the drive shaft 4 drives a cone 7 whose apex substantially corresponds to the center of the joint 5.
  • the cone 7, which has a radius r, is strongly pressed by centrifugal force against the surface of an inner cone 8 of radius R, upon which surface it rolls when the drive shaft 4 rotates.
  • the apex of cone 8 likewise is located at the center of the universal joint 5.
  • the axis of cone 7 describes a cone of revolution with a speed to, such that if drive shaft 4 turns at a speed n:
  • the centrifugal force F will be proportional to the mass m of cone 7, to the square of w, and to (--r) or the radius of circumference described by the center from which it is apparent that the centrifugal force F can be given as high a value as necessary by reducing the value of the denominator (R-r), that is to say, by reducing the difference between the diameters r and R of cones 7 and 8, respectively.
  • this converter is connected between an electric mot-or or an internal combustion engine and a machine having inertia, the torque required of the motor or engine will be very small when it is started up, resulting in a very considerable simplification, or even in the complete elimination, of the starting up arrangement for the machine.
  • the coefficient of friction f varies according to the material constituting the rolling surfaces, which can be steel, rubber, or any other material capable of sustain- 4 ing pressure and of transmitting by friction a tangential force.
  • FIGURE 9 illustrates one simple way of changing the direction of rotation of the output shaft with respect to the input shaft, without stopping the latter.
  • the drive cone 1"! is coupled to the input or drive shaft 4, and the driven ring 23 consists of two conical portions: a portion 1%, for regular operation, of which the apex is located at the common center of the joints of the shafts, and a portion 19 oppositely inclined with respect to 18.
  • Conical zones 20 and 21, supported by the reactor 24, can be moved apart or together, under control of the operator, along the axial direction. When they are moved together, zones 19 and 21 are brought into contact, and the driven member 23 turns in i the opposite direction of that of the driving cone 17.
  • the reaction cone is made radially movable.
  • This mobility can be obtained in the same way as for the other cones, that is, to joint the reaction cone about a central point of a universal joint or of an elastic joint.
  • this point is located near the apices of the other cones. The arrangement is shown in FIGURE 6.
  • the input shaft 4 is connected to the driving ring or cone -1 by means of a universal joint 5.
  • the reaction ring or cone 3 is connected to the housing 13 of the converter by means of a universal joint 14, and the driven ring 2 is connected to the driven shaft 12 through a universal joint 11.
  • These universal joints being so well known, they are illustrated only schematically. 'Moreover, they can be replaced by other kinds of mechanical joints or by known elastic joints that permit the necessary conical clearance.
  • FIGURE 7 The relative positions taken by the three rings during operation are shown schematically in FIGURE 7.
  • the center of gravity of the group of three rings 1, 2, and 3 is G.
  • the centers of rings 1, 2, and 3 are 0, P, and Q, respectively.
  • Point A identifies the point of contact between the driving and driven rings 1 and 2 and point B that between the driven and reaction rings 2 and 3.
  • the centrifugal force exerted by each ring is represented by a vector passing through the center of the respective ring and through the combined center of gravity G.
  • the center of gravity G is substantially motionless dur ing operation.
  • the springs are designed so that the natural frequency of the suspension of the three rings is much lower than the lowest frequency of conical rotation to encountered in use.
  • the residual radial forces acting on joints 5, 11, and 14 can be reduced by taking into account the two principal inertias of the rings and choosing a suitable position for the contact Zones with respect to the location of the center of gravity G and of these joints.
  • the ratio between the input and output speeds can be varied during operation or even when the input or drive shaft is stopped. In the embodiment of FIGURE 6, for example, it suffices to move the driven ring 2 axially.
  • This embodiment lends itself particularly well to the simple control of the reduction ratio of the speed and torque, for example, of the input shaft.
  • FIGURE 10 illustrates an embodiment using weights 25, similar to the scheme of known centrifugal governors, acting on the axial movement of the driven ring 2.
  • Such a control can be used advantageously in motor vehicles powered by heat engines or electric motors, because the transmission ratio is automatically adjusted to the road conditions.
  • the converter allows maximum use of the braking action of the motor when going down hill and to slow down the vehicle until it is stopped dead, if necessary.
  • FIGURES 1, 7, and 12 illustrate an arrangement of the drive element 1, the driven element 2, and the reactor 3 which permit varying the speed ratio N/n between the output and input shafts from zero to one, the latter limit corresponding to direct transmission.
  • the driven element is located between the driver and the reactor.
  • FIGURES 11 to 19 Other embodiments lying within the scope of the invention are shown, by way of example, in FIGURES 11 to 19. They permit to obtaining of other features that can be used in Whole or in part.
  • reaction ring 3 is located between the drive ring 1 and the driven ring 2. These two embodiments have the special property that the ratio N/n of the output to the input speed can be varied from zero to infinity.
  • the sense of rotation of the driven ring 2 is the opposite of that of the drive ring 1.
  • the drive ring 1 is located between the driven ring 2 and the reactor 3.
  • the possible variation of N/n extends from one to infinity.
  • the drive and driven rings 1 and 2 rotate in the same direction.
  • the driving and driven members 1 and 2 respectively, roll side by side on the inner surface of the reactor 3.
  • the ratio of N/n varies from zero to infinity.
  • the rotation of the members 1 and 2 can be in the same, or in opposite, directions.
  • the driven ring 2 and the reactor ring 3 roll inside of the drive ring.
  • the ratio N/n of the output speed and the input speed can vary from one to zero and from zero to less than infinity. This embodiment permits, in particular, to progressively change from direct transmission to a complete stop to operation in reverse.
  • FIGURE 21 shows a variation of this embodiment.
  • FIGURE 18 in which the drive and reactor rings roll inside of the driven ring, allows of the obtaining of N/n ratios from one to zero.
  • FIGURE 19 shows one possible embodiment where the driving member 1 is not coaxial with the driven member 2.
  • the reactor 3 acting somewhat as a drive rod, transmits the impulses to member 2 that it receives from the drive member 1.
  • the ratio N/n ranges from zero to infinity.
  • the output shaft can rotate in either direction and is determined when starting up.
  • FIGURE 20 Schematically shows an embodiment particularly suitable for greatly reducing or stepping up the speed of the output shaft.
  • the input shaft 30 transmits the drive rotation to shaft 31 through a universal joint 32 or an equivalent elastic joint.
  • Shaft 31 is positioned by a bearing 33 and carries at its one end an eccentric weight 34.
  • the weight 34 transmits a conical rotation, having a speed to about the center IX of the universal joints 32 and 37, to the axis XX that is common to shaft 31, cone 35, and hollow shaft 36.
  • the cone 35 is thus constrained to roll on the inside surface of the reactor cone 3 and to turn about its axis of revolution at the out put speed N which it imparts t-o shaft 29.
  • the formula giving the output speed N as a function of w is the same as that shown earlier:
  • Shaft 29 becomes the input shaft and shaft 30 the output shaft.
  • FIGURE 20 The reactor 3 can be fixed on a base or elastically suspended and connected to the mount through a universal joint aligned with the universal joints 32 and 37' in the same manner as in FIGURES 6, 10, and 21.
  • the change in the diameter of the rolling path, obtained by the axial movement of the rings can also be obtained by the axial movement of one or two rings.
  • the treads can have double tapers or conicities or even be replaced by portions of cylinders, without departing from the spirit and scope of the invention, although where treads or rolling paths are conical or where the point of contact is. conical it is advantageous to eliminate friction by bringing the apices of these cones as close together as possible.
  • FIGURE 23 illustrates an embodiment of the invention in which the rings roll while remaining parallel to the same fixed plane, thanks to the use of shafts with two universal joints.
  • FIGURE 24 shows an arrangement of the invention in which the outer ring happens to be, by way of example only, the reactor ring 3, which receives only balanced forces, since both the driving and driven members are doubled.
  • Each driving ring 1a and 1b and each driven ring 2a and 2b is shifted from the other 180 along the path of rotation.
  • the two driven rings 2a and 2b are connected by an Oldham coupling 28 or an equivalent arrangement capable of transmitting a torque between two shafts olfset radially.
  • FIGURE 22 illustrates the principle of this embodiment in the instance of two driven rings.
  • the combination of parts 2 and 12 duplicates that of 2 and 12.
  • a torque variable converter comprising at least one rotating first drive means; at least one rotatable second driven means; third means for absorbing the differences between the torques applied to the first and second means; means for transferring power from said first means to said second means, including three surface means in cooperative association, one defined by each of said three means; at least one of said three surface means being at least one inner surface defining a radius of curvature and acting as an endless rolling path for at least one other of said surface means defining a smaller radius, whereby the corresponding means of each of said at least one other surface means is made to rotate about itself and to roll about the said at least one inner surface under the influence of centrifugal force at least one of said surface means having a double taper to permit reversal of direction of rotation of said second means, each taper corresponding to one direction of rotation, said double taper being located on said second means and including a first and sec ond oppositely conical portions, and said third means including first and second oppositely conical portions cooperating respectively with said first and second portions of said double taper
  • a torque variable converter comprising at least one rotating first drive means; at least one rotatable second driven means, third means for absorbing the differences between the torques applied to the first and second means; means for transferring power from said first means to said second means, including three surface means in cooperative association, one defined by each of said three means; at least one of said three surface means being at least one inner surface defining a radius of curvature and acting as an endless rolling path for at least one other of said surface means defining a smaller radius, whereby the corresponding means of each of said at least one other surface means is made to rotate about itself and to roll about the said at least one inner surface under the influence of centrifugal force, each of said three means having a surface of revolution, including said at least one inner surface and said at least one other surface means, which defines an axis of which surfaces at least two have different radii; two of said three means, including said corresponding means, rotating and rolling on endless paths at least one of them under the influence of centrifugal force, the surface of said third means being located between the surfaces
  • a torque and speed converter comprising a first shaft, a framework and a second shaft; said first shaft in cluding a joint; a first ring member integrally rotating with the first shaft through said joint enabling the first ring member to have, a radial or conical freedom to effect a composite movement comprising, on one hand, a rotation linked through said joint to that of said first shaft and, on the other hand, a planetary rotation about said first shaft; 2.
  • a torque and speed converter comprising a first shaft, a framework and a secon dshaft; said first shaft including a joint; a first ring member having at least one surface of revolution integrally rotating with the first shaft through said joint enabling the first ring member to have a radial or conical freedom to effect a composite movement comprising, on one hand, a rotation linked through said joint to that of said first shaft and, on the other hand, a planetary rotation about said first shaft; a second, reacting ring member rotating integrally with the framework and comprising at least one surface of revolution; said second shaft including a further joint; and a third ring member having at least one surface of revolution rotatable integrally with said second shaft through said further joint enabling the third ring member to have a radial or conical freedom to roll according to a composite motion comprising, on one hand, a rotation in connection with said second shaft owing to said further joint and, on the other hand, a planetary rotation of its center having the same speed as that of the planetary rotation of
  • a torque and speed converter comprising a first shaft, a framework and a second shaft; said first shaft including a joint; a first ring member having at least one surface of revolution integrally rotating with the first shaft through said joint enabling the first ring member to have a radial or conical freedom to effect a composite movement comprising, on one hand, a rotation linked through said joint to that of said first shaft and, on the other hand, a planetary rotation about said first shaft; a second, reacting ring member rotating integrally with the framework and comprising at least one surface of revolution; said second shaft including a further joint; and a third ring member having at least one surface of revolution rotatable integrally with said second shaft through said, further joint enabling the third ring member to have a radial or conical freedom to roll according to a composite motion comprising, on one hand, a rotation in connection with said second shaft owing to said further joint and, on the other hand, a planetary rotation of its center having the same speed as that of the planetary rotation of said first first
  • a torque and speed converter comprising a first shaft, a framework and a second shaft; said first shaft including a jint;'a first ring member having at least one surface of revolution integrally rotating with the first shaft through said joint enabling the first ring member to have a radial or conical freedom to effect a composite movement comprising, on one hand, a rotation linked through said joint to that of said first shaft and, on the other hand, a planetary rotation about said first shaft; a second, reacting ring member rotating integrally with the framework and comprising at least one surface of revolution; said second shaft including a further joint; and a third ring member having at least one surface of revolution rotatable integrally with said second shaft through said further joint enabling the third ring member to have aradial or conical freedom to roll according to a composite motion comprising, on one hand, a rotation in connection with said second shaft owing to said further joint and, on the other hand, a planetary rotation of its center having the same sped as that of the planetary
  • a torque and speed converter comprising a first shaft, a framework and a second shaft; said first shaft including a joint; a first ring member having at least one surface of revolution integrally rotating with the first shaft through said joint enabling the first ring member to have a radial or conical freedom to effect a composite movement comprising, on one hand, a rotation linked through said joint to that of said first shaft and, on the other hand, a planetary rotation about said first shaft; a second, reacting ring member rotating integrally with the framework and comprising at least one surface of revolution; said second shaft including a further joint; and a third ring member having at least one surface of revolution rotatable integrally with said second shaft through said further joint enabling the third ring member to have a radial or conical freedom to roll according to a composite motion comprising, on one hand, a rotation in connection with said second shaft owing to said further joint and, on the other hand, a planetary rotation of its center having the same speed as that of the planetary rotation of said first ring
  • a torque variable converter comprising at least one rotating first drive means; at least one rotatable second driven means; third means for absorbing the diiferences between the torques applied to the first and second means; means for transferring power from said first. means to said second means, including three surface means in cooperative association, one defined by each of said three means; at least one of said three surface means being at least one inner surface defining a radius of curvature and acting as an endless rolling path for at least one other of said surface means defining a smaller radius, whereby the corresponding means of each of said at least one other surface means is made to rotate about itself and to roll about the said at least one inner surface under the influence of centrifugal force; each of said three means having a surface of revolution, including said at least one inner surface and said at least one other surface means, which defines an axis, of which surfaces at least two have diiferent radii; two of said three means, including said corresponding means, rotating and rolling on endless paths, at least one of them under the influence of centrifugal force; said surfaces
  • a torque and speed converter comprising a first shaft, a framework and a second shaft; said first shaft including a joint; a first ring member having at least one surface of revolution integrally rotating with the first shaft through said joint enabling the first ring member to have a radial or conical freedom to effect a composite movement comprising, on one hand, a rotation linked through said joint to that of said first shaft and, on the other hand, a planetary rotation about said first shaft; a second, reacting ring member rotating integrally with the framework and comprising at least one surface of revolution; said second shaft including a further joint; and a third ring member having at least one surface of revolution rotatable integrally with said second shaft through said further joint enabling the third ring member to have a radial or conical freedom to roll according to a composite motion comprising, on one hand, a rotation in connection with said second shaft owing to said further joint and, on the other hand, a planetary rotation of its center having the same speed as that of the planetary rotation of said first ring
  • a torque and speed converter comprising a first shaft, a. framework and a second shaft; said first shaft including a joint; a first ring member having at least one surface of revolution integrally rotating with the first shaft through said joint enabling the first ring member to have a radial or conical freedom to effect a composite movement comprising, on one hand, a rotation linked through said joint to that of said first shaft and, on the other hand, a planetary rotation about said first shaft; 21 second, reacting ring member rotating inte rally with the framework and comprising at least one surface of revolution; said second shaft including a further joint; and a third ring member having at least one surface of revolution rotatable integrally with said second shaft through said further joint enabling the third ring member to have a radial or conical freedom to roll according to a composite motion comprising, on one hand, a rotation in connection with said second shaft owing to said further joint and, on the other hand, a planetary rotation of its center having the same speed as that of the planetary rotation of said first first
  • a torque and speed converter comprising a first shaft, a framework and a second shaft; said first shaft in cluding a joint; a first ring member having at least one surface of revolution integrally rotating with the first shaft through said joint enabling the first ring member to have a radial or conical freedom to effect a composite movement comprising, on one hand, a rotation linked through said joint to that of said first shaft and, on the other hand, a planetary rotation about said first shaft; a second, reacting ring member rotating integrally with the framework and comprising at least one surface of revolution; said second shaft including a further joint; and a third ring member having at least one surface of revolution rotatable integrally with said second shaft through said further joint enabling the third ring member to have a radial or conical freedom to roll according to a composite motion comprising, on one hand, a rotation in, connection with said second shaft owing to said further joint and, on the other hand, a planetary rotation of its center having the same speed as that of the planetary rotation
  • a torque and speed converter comprising a first shaft, a framework and a second shaft; said first shaft in: cluding a joint; a diametrically opposed pair of first ring members each having at least one surface of revolution integrally rotating with the first shaft through said joint enabling them to have a radial or conical freedom to effect a composite movement comprising, on one hand, a rotation linked through said joint to that of said first shaft and, on the other hand, a planetary rotation about said first shaft; a second, reacting ring member rotating inter grally with the framework and comprising at least one surface of revolution; said second shaft including a further joint; and a diametrically opposed pair of third ring members each having at least one surface of revolution rotatable integrally with said second shaft through said further joint enabling the third ring members to have a radial or conical freedom to roll according to a composite motion comprising, on one hand, a rotation in connection with said second shaft owing to said further joint and, on the other hand, a planetary rotation of
  • a torque variable converter comprising at least one rotating first drive means; at least one rotatable second driven means; third means for absorbing the differences between the torques applied to the first and second means; means for transferring power from said first means to said second means, including three surface means in cooperative association, one defined by each of said three means; at least one of said three surface mean being at least one inner surface defining a radius of curvature and acting as an endless rolling path for at least one other of said surface means defining a smaller radius, whereby the corresponding means of each of said at least one other surface means is made to rotate about itself and to roll about said at least one inner surface under the influence of centrifugal force; each of said three means having a surface of revolution, including said at least one inner surface and said at least one other surface means which defines an axis, of which surfaces at least two have different radii; two of said three means, including said corresponding means, rotating and rolling on endless paths at least one of them under the influence of centrifugal force; said second means being doubled; and said third means having
  • a torque variable converter comprising at least one rotating first drive means; at least one rotatable second driven means; third means for absorbing the differences between the torques applied to the first and second means; means for transferring power from said first means to said second means, including three surface means in cooperative association, one defined by each of said three means; at least one of said three surface means being at least one inner surface defining a radius of curvature and acting as an endless rolling path for at least one other of said surface means defining a smaller radius, whereby the corresponding means of each of said at least one other surface means is made to rotate about itself and to roll about said at least one inner surface under the influence of centrifugal force; each of said three means having a surface of revolution, including said at least one inner surface and said at least one other surface means which defines an axis, of which surfaces at least two have different radii; two of said three means, including said corresponding means, rotating and rolling on endless paths at least one of them under the influence of centrifugal force; said second means being doubled; said third means having an

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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US263163A 1962-03-13 1963-03-06 Torque converter Expired - Lifetime US3227004A (en)

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FR890841A FR1338321A (fr) 1962-03-13 1962-03-13 Convertisseur de couple

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US3227004A true US3227004A (en) 1966-01-04

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US (1) US3227004A (de)
AT (1) AT245888B (de)
CH (1) CH399109A (de)
DE (1) DE1425780B2 (de)
FR (1) FR1338321A (de)
GB (1) GB1040064A (de)
NL (1) NL142481B (de)

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US3442158A (en) * 1967-03-21 1969-05-06 Ernst Marcus Stepless variable transmission
US3910137A (en) * 1972-11-17 1975-10-07 Nedeljkovitch R Rotative transmissions at infinitely varying ratios
US4682517A (en) * 1985-01-16 1987-07-28 Frederick Manufacturing Company, Inc. Variable speed drive--apparatus and method of fabricating the apparatus
EP0263201A1 (de) * 1986-10-03 1988-04-13 T R & R ASSOCIATES Kegelgetriebe
US5582556A (en) * 1995-05-03 1996-12-10 Phung; Viet Variable ratio transmission
WO2001044688A1 (en) * 1999-12-17 2001-06-21 Hostin, Stanislav Step-up gearing

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US4491033A (en) * 1983-06-23 1985-01-01 Usm Corporation Double eccentric wave generator arrangement
GB8716023D0 (en) * 1987-07-08 1987-08-12 British Petroleum Co Plc Transmission system
EP0933560B1 (de) * 1998-01-28 2002-06-12 Alfredo Amisano Stufenloses mechanisches Getriebe für eine Antriebswelle für Werkzeugmaschinen oder Kraftfahrzeuge
CZ286542B6 (cs) * 1998-08-07 2000-05-17 Miroslav Ing. Csc. Sedláček Zařízení pro změnu otáček

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DE534341C (de) * 1928-01-15 1931-09-25 Heinrich Schieferstein Verfahren zur Umwandlung von im Kreise schwingender Energie in Drehenergie
CH161130A (fr) * 1928-05-15 1933-04-15 Bedu Clet Changement de vitesse.
US2012629A (en) * 1932-08-19 1935-08-27 Karl K Huppmann Internal reversible multispeed driving mechanism
US2035582A (en) * 1934-10-15 1936-03-31 Guy H Hall Variable ratio transmission device
GB506655A (en) * 1937-12-01 1939-06-01 Charles Samuel Johnson An improved speed reduction gear
US2328536A (en) * 1941-09-15 1943-09-07 Falk Corp Variable speed transmission
DE897941C (de) * 1951-10-28 1953-11-26 Wolfgang Dr-Ing Herbold Reibradgetriebe fuer grossen UEbersetzungsbereich
US2831373A (en) * 1953-06-11 1958-04-22 Graham Transmissions Inc Variable speed friction gearing
US3035459A (en) * 1958-05-31 1962-05-22 Legros Robert Guy Automatic variable ratio transmission device for vehicles and other applications
US3085450A (en) * 1960-09-23 1963-04-16 Graham Transmissions Inc Transmission
US3119283A (en) * 1962-04-23 1964-01-28 Gen Motors Corp Power transmission

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE534341C (de) * 1928-01-15 1931-09-25 Heinrich Schieferstein Verfahren zur Umwandlung von im Kreise schwingender Energie in Drehenergie
CH161130A (fr) * 1928-05-15 1933-04-15 Bedu Clet Changement de vitesse.
US2012629A (en) * 1932-08-19 1935-08-27 Karl K Huppmann Internal reversible multispeed driving mechanism
US2035582A (en) * 1934-10-15 1936-03-31 Guy H Hall Variable ratio transmission device
GB506655A (en) * 1937-12-01 1939-06-01 Charles Samuel Johnson An improved speed reduction gear
US2328536A (en) * 1941-09-15 1943-09-07 Falk Corp Variable speed transmission
DE897941C (de) * 1951-10-28 1953-11-26 Wolfgang Dr-Ing Herbold Reibradgetriebe fuer grossen UEbersetzungsbereich
US2831373A (en) * 1953-06-11 1958-04-22 Graham Transmissions Inc Variable speed friction gearing
US3035459A (en) * 1958-05-31 1962-05-22 Legros Robert Guy Automatic variable ratio transmission device for vehicles and other applications
US3085450A (en) * 1960-09-23 1963-04-16 Graham Transmissions Inc Transmission
US3119283A (en) * 1962-04-23 1964-01-28 Gen Motors Corp Power transmission

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3442158A (en) * 1967-03-21 1969-05-06 Ernst Marcus Stepless variable transmission
US3910137A (en) * 1972-11-17 1975-10-07 Nedeljkovitch R Rotative transmissions at infinitely varying ratios
US4682517A (en) * 1985-01-16 1987-07-28 Frederick Manufacturing Company, Inc. Variable speed drive--apparatus and method of fabricating the apparatus
EP0263201A1 (de) * 1986-10-03 1988-04-13 T R & R ASSOCIATES Kegelgetriebe
US5582556A (en) * 1995-05-03 1996-12-10 Phung; Viet Variable ratio transmission
WO2001044688A1 (en) * 1999-12-17 2001-06-21 Hostin, Stanislav Step-up gearing

Also Published As

Publication number Publication date
NL142481B (nl) 1974-06-17
AT245888B (de) 1966-03-25
DE1425780A1 (de) 1968-12-05
GB1040064A (en) 1966-08-24
DE1425780B2 (de) 1970-09-17
CH399109A (fr) 1966-03-31
FR1338321A (fr) 1963-09-27

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