GB1599953A - Traction controlled in-line transmission - Google Patents

Traction controlled in-line transmission Download PDF

Info

Publication number
GB1599953A
GB1599953A GB12566/78A GB1256678A GB1599953A GB 1599953 A GB1599953 A GB 1599953A GB 12566/78 A GB12566/78 A GB 12566/78A GB 1256678 A GB1256678 A GB 1256678A GB 1599953 A GB1599953 A GB 1599953A
Authority
GB
United Kingdom
Prior art keywords
roller
drive
gear
transmission
traction
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
Application number
GB12566/78A
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BALES MCCOIN RESEARCH Inc
Original Assignee
BALES MCCOIN RESEARCH Inc
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.)
Filing date
Publication date
Priority claimed from US05/787,372 external-priority patent/US4192201A/en
Application filed by BALES MCCOIN RESEARCH Inc filed Critical BALES MCCOIN RESEARCH Inc
Publication of GB1599953A publication Critical patent/GB1599953A/en
Expired legal-status Critical Current

Links

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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H37/0853—CVT using friction between rotary members having a first member of uniform effective diameter cooperating with different parts of a second 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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/16—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a conical friction surface
    • F16H15/18—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a conical friction surface externally
    • F16H15/20—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a conical friction surface externally co-operating with the outer rim of the member A, which is perpendicular or nearly perpendicular to the friction surface of the member B
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
  • Transmission Devices (AREA)
  • Structure Of Transmissions (AREA)

Description

(54) TRACTION CONTROLLED IN-LINE TRANSMISSION (71) We, BALES McCOIN RE SEARCH INC., a Corporation organised and existing under the laws of the State of Texas, United States of America, of 4401, Montana, El Paso, Texas 79903, United States of America, do hereby declare the invention for which we pray that a patent may be granted to us, and the method by which it is to be described, to be particularly described in and by the following statement: This invention relates to variable speed transmissions.
In British Patent Application No. 34029/ 77 Serial No. 1,582,665 the transmission disclosed featured a traction drive assembly through which a small fraction of the total torque transmitted by the transmission is utilised to vary and establish the overall transmission drive ratio in a practical and efficient manner by providing a favourable relationship between the drive ratio and the contact pressure in the traction drive assembly. The traction drive assembly is positioned in laterally spaced relationship to the transmission gearing and includes a driven traction roller axially shiftable along a fixed path parallel to the common rotational axis for the transmission input and output shafts. The other traction roller of variable diameter is mounted on a pivotally displaceable bracket for limited corrective displacement during axial shift of the driven roller engaged therewith to vary the drive ratio.
According to the present invention, there is provided a change speed transmission, comprising input and output members, a power transmitting gear arrangement directly drivingly interconnecting said input and output members for establishing a relatively high torque power transmission path therebetween, a biasing gear arrangement directly drivingly connected to the input member and coupled with the power transmitting gear arrangement for establishing the drive ratio through the power transmission path between the input and output members, and a variable traction drive as herein defined directly driven by the input member and coupled with the torque biasing gear arrangement whereby variation of the vari able traction drive in use of the transmission will control the torque biasing arrangement to vary said drive ratio, means being provided for varying the contact force between the traction roller and the driven roller of the variable traction drive in accordance with the torque being transmitted through the power transmitting gear arrangement. When referring herein to a variable traction drive we are referring to a drive comprising a traction roller the diameter of which varies along the axial length and a driven roller engageable with the traction roller at varying locations along the length to vary the speed ratio of the traction and driven rollers.
In the preferred embodiment the traction drive includes a roller, whose diameter varies along its length driven by an input shaft about the rotational axis common to the input and an output shaft. A driven traction roller is mounted on a pivotal bracket and is axially shiftable along its spline shaft to change the transmission drive ratio. Contact pressure be tween the rollers is changed as a function of the driven roller position and the pitch line curvatures of the rollers at the contact zone.
The contact pressure is thereby varied in an optimum manner characterised by a minimum pressure in the neutral position of the driven roller as predetermined by the torque trans mission drive relationships in the power trans mitting gearing which is axially aligned with the variable diameter traction roller. As an alternative, the axially shiftable roller could be rotatable about a fixed axis common with the input and output shafts while the variable dia meter roller is mounted at an angle thereto on the bracket. In the latter arrangement, a plu rality of variable diameter rollers could be mounted by a-plurality of brackets for drive engagement with the axially shiftable roller in order to distribute the torque load and thereby increase the load capacity of the transmission.
Power transmission through the gearing may be interrupted by release of a hydrostatic brake holding a floating carrier for a gear train inter connecting orbit gears in the power trans mitting gear assembly of the transmission.
The invention will be further described with reference to the accompanying drawings, in which: Figure 1 is a somewhat simplified and partially schematic side elevational view of an embodiment of transmission in accordance with the present invention; Figure 2, 3 and 4 are enlarged partial sectional views of the gearing taken substantially on planes indicated by section lines 2-2, 3-3 and 4-4 in Figure 1; Figure 5 is an enlarged partial sectional view of the traction drive assembly taken substantially through a plane indicated by section line 5-5 in Figure 1; Figure 6 is a graph showing various operational relationships associated with the transmission of Figure 1.
Referring now to Figure 1 in particular, the transmission 12 includes an input shaft 16 and an axially aligned output shaft 18.
The input shaft is directly connected to an infinitely variable traction drive assembly generally referred to by reference numeral 42 through which selection of the over-all transmission drive ratio is effected. A power transmitting gear assembly 40 drivingly interconnects the input and output shafts while torque bias control means 44 in the form of epicyclic gearing drivingly interconnects the variable traction drive assembly 42 with the power transmitting gear assembly 40. The torque bias control means 44 is arranged to reduce the load and power requirements which would be ordinarily expected to be imposed on the variable traction drive assembly if it were to act directly on the main power transmitting gearing 40 in performing its drive ratio changing function for the over-all transmission.
Thus the input shaft is directly connected to all three of the variable traction drive assembly 42, the torque bias means 44 and the power transmitting gear assembly 40 with the assembly 42 using a relatively low power and torque transmission to control the bias means 44 which has a capability of applying a relatively higher torque to control the speed ratio of the assembly 40.
As more clearly seen in Figures 1, 3 and 4, the power transmitting gear assembly 40 includes a differential planetary gear set 46 formed by a sun gear 48 fixed to the inner end of the input shaft 16. The sun gear 48 is in constant mesh with planet gears 50 rotatably mounted on a carrier 52. The planet gears 50 also mesh with an internal orbit gear 54 having external gear teeth 56 enmeshed with a floating gear train comprising intermeshing gears 58, 60, drivingly connecting the orbit gear 54 to orbit gear 64 associated with a power path combining planetary gear set 66.
The gear train includes intermeshing gears 58 and 60. The parallel axes of the gears in this gear train are rotatable on a carrier 62 adapted to be retarded against rotation by a hydrostatic braking device 74 of any well-known type connected to a closed fluid control circuit 22. The gear set 66 includes planet gears 68 in constant mesh with the orbit gear 64 and rotatably mounted on a carrier 70 fixed to the output shaft 18. The planet gears 68 are also in mesh with a sun gear 72 that is fixed to the carrier 52 ef the differential gear set 46.
It will be apparent that the input shaft 16 will transmit torque through the gear set 46 at a drive ratio dependent on the rotational speed of the carrier 52 relative to the sun gear 48. The carrier 52 is, therefore, rotated at a lower speed than the input shaft to enable transmission of high torque through gear set 46 to the orbit gear 54 under control of a relatively low torque drive through the variable traction drive assembly 42. The power path through which low torque is transmitted to the carrier 52 for drive ratio control purposes terminates at the sun gear 72 of gear set 66 to which high torque is transmitted from orbit gear 54 through the gear train formed by gears 58, 60 and 61 when the floating gear carrier 62 is held stationary by the hydrostatic brake 74. Manual or override control over the transmission may be exercised through the hydrostatic brake by means of its fluid control circuit 22. A neutral and drive control valve assembly 24 may accordingly be associated with the fluid circuit to selectively restrict flow therein. A spring or automatically biased torque control valve 26 may also be connected in parallel with the control valve assembly 24.
Shock protection is provided by an accumulator 28. A pressure sensor 29 connected to the fluid circuit will be effective to monitor the torque transmitted through the gearing and thereby supply a signal to an automatic control 30 for changing the spring tension of the device 152 to vary the contact pressure between the surfaces 154 and 156 in order to compensate for abrupt increases in torque loading on the transmission. Other control arrangements may, of course, be utilised for the brake device 74. A parking brake element 80 is also provided on the output shaft 18.
It will be apparent that a suitable housing will be provided for the transmission hereinbefore described, constituting the stationary frame for the gearing. The housing frame supports a fixed pivot 92 about which a slide bracket 120 is pivotally displaceable in a pivotal plane intersecting the common rotational axis of the input and output shafts. The slide bracket 120 rotatably mounts an elongated position control screw 124 by means of spaced bearings carried by the bracket 120. The screw 124 is threadedly engaged with a carriage 112 as shown in Figures 1 and 5 for displacement of a traction roller element 110 axially along a shaft 118 to which it is splined. The shaft 118 is rotatably mounted on the bracket 120 by a bearing 90 for rotation about an axis parallel to that of the screw shaft 124. A suitable coupling joint 100 connects the spline shaft 118 to a gear 132 for transmitting a low control torque to the torque bias control means 44. Gear 132 and gear 134 with which it is enmeshed are fixed axes gears for transmitting the low torque to an orbit gear 136 associated with the torque bias control means 44. The orbit gear 136 is in constant mesh with planet gears 138 as shown in Figures 1 and 2, said planet gears being rotatably mounted on the same carrier 52 associated with the power transmitting gear assembly 40. A sun gear 140 fixed to the input shaft 16 meshes with the planet gear 138.
The traction roller element 110 which is of substantially constant drive diameter is held in frictional drive engagement with a variable diameter traction drive element 94 fixed to the input shaft for rotation therewith about the central rotational axis of the transmission.
An adjustable tension device 152, such as that disclosed in my prior copending Application aforementioned, bears against the pivotal slide bracket 120 so as to establish the drive engaging pressure between the traction roller elements 110 and 94 at their zone of contact.
The zone of contact is, of course, shifted by rotation of the screw shaft 124 so as to change the transmission drive ratio and will at the same time change the leverage ratio through which the tension device 152 exerts its force at the zone of contact. Therefore, the contact force will vary for each position of the roller element 110 in accordance with some nonlinear function as depicted by curve 168 in Figure 6. The geometry of the arrangement described is such that the minimum point 170 on the curve 168 coincides with the neutral condition of the transmission corresponding to a zero drive ratio, the drive ratio being reflected on the ordinate 162. The drive ratio is proportional to the displacement of the roller element 110 as depicted by the straight line curve 158 plotted against the roller element position on the abscissa 160.
The roller element 110 is shifted along shaft 118 between one limit position as shown in Figure 1 at which the roller elements are of equal diameter as shown by way of example to an opposite limit position at which the diameter of roller element 94 is substantially greater than that of roller element 110 in order to vary the drive ratio in the drive assembly 42 and thereby vary the over-all transmission drive ratio as aforementioned. Ordinarily the roller elemcnts engage each other along a straight or constant conical pitch line corresponding to the pitch angle between the rotational axes of the input shaft 16 and the roller spline shaft 118. In order to meet varying torque requirements, the pitch line along which the roller elements engage each other is varied by providing the roller element 94 with a vari able pitch curvature 154. The curvature 154 may be designed to effect a change in contact pressure as a function of the transmission drive ratio. A crown curvature 156 also deviating from the basic pitch angle is provided for the roller element 110. A small amount of pivotal displacement of the roller element 110 about pivot 92 occurs during movement of the roller element 110 between its limit positions for corrective variation in the basic pitch angle from which the roller curvatures 154 and 156 deviate. The curvatures 154 and 156 are theoretically tangent to each other at the contact zone between the roller surfaces for all positions of the roller 110 to minimise slippage. Some corrective modification of the curvature 156 may also be necessary to maintain the intersection between the rotational axis of roller 94 and the pitch line at a constant distance from the pivot point of pivot 92 in order to minimise normal spin moment of traction. Such error compensation will result in some variation in the contact zone area between the engaging roller elements to affect the contact pressure for any given contact force exerted by the tension device 152 at the variable leverage aforementioned. The resultant contact pressure, dependent on such vari ables as the contact force, the contact zone area, the roller curvatures and the leverage ratio will vary as a function of the displacement of the roller 110 as depicted by curve 174 in Figure 6. As shown, this resultant pressure curve 174 also has a minimum peak at the neutral position of the roller 110.
WHAT WE CLAIM IS: 1. A change speed transmission, comprising input and output members, a power transmitting gear arrangement directly drivingly interconnecting said input and output members for establishing a relatively high torque power transmission path therebetween, a biasing gear arrangement directly drivingly connected to the input member and coupled with the power transmitting gear arrangement for establishing the drive ratio through the power transmission path between the input and output members, and a variable traction drive as herein defined directly driven by the input member and coupled with the biasing gear arrangement whereby variation of the variable traction drive in use of the transmission will control the torque biasing arrangement to vary said drive ratio, means being provided for varying the contact force between the traction roller and the driven roller of the variable traction drive in accordance with the torque being transmitted through the power transmitting gear arrangement.
2. A transmission according to claim 1, wherein said traction drive further includes a driven roller in engagement with the traction roller which is rotatable about a fixed axis common to the input and output members,
**WARNING** end of DESC field may overlap start of CLMS **.

Claims (9)

  1. **WARNING** start of CLMS field may overlap end of DESC **.
    by a bearing 90 for rotation about an axis parallel to that of the screw shaft 124. A suitable coupling joint 100 connects the spline shaft 118 to a gear 132 for transmitting a low control torque to the torque bias control means 44. Gear 132 and gear 134 with which it is enmeshed are fixed axes gears for transmitting the low torque to an orbit gear 136 associated with the torque bias control means 44. The orbit gear 136 is in constant mesh with planet gears 138 as shown in Figures 1 and 2, said planet gears being rotatably mounted on the same carrier 52 associated with the power transmitting gear assembly 40. A sun gear 140 fixed to the input shaft 16 meshes with the planet gear 138.
    The traction roller element 110 which is of substantially constant drive diameter is held in frictional drive engagement with a variable diameter traction drive element 94 fixed to the input shaft for rotation therewith about the central rotational axis of the transmission.
    An adjustable tension device 152, such as that disclosed in my prior copending Application aforementioned, bears against the pivotal slide bracket 120 so as to establish the drive engaging pressure between the traction roller elements 110 and 94 at their zone of contact.
    The zone of contact is, of course, shifted by rotation of the screw shaft 124 so as to change the transmission drive ratio and will at the same time change the leverage ratio through which the tension device 152 exerts its force at the zone of contact. Therefore, the contact force will vary for each position of the roller element 110 in accordance with some nonlinear function as depicted by curve 168 in Figure 6. The geometry of the arrangement described is such that the minimum point 170 on the curve 168 coincides with the neutral condition of the transmission corresponding to a zero drive ratio, the drive ratio being reflected on the ordinate 162. The drive ratio is proportional to the displacement of the roller element 110 as depicted by the straight line curve 158 plotted against the roller element position on the abscissa 160.
    The roller element 110 is shifted along shaft 118 between one limit position as shown in Figure 1 at which the roller elements are of equal diameter as shown by way of example to an opposite limit position at which the diameter of roller element 94 is substantially greater than that of roller element 110 in order to vary the drive ratio in the drive assembly 42 and thereby vary the over-all transmission drive ratio as aforementioned. Ordinarily the roller elemcnts engage each other along a straight or constant conical pitch line corresponding to the pitch angle between the rotational axes of the input shaft 16 and the roller spline shaft 118. In order to meet varying torque requirements, the pitch line along which the roller elements engage each other is varied by providing the roller element 94 with a vari able pitch curvature 154. The curvature 154 may be designed to effect a change in contact pressure as a function of the transmission drive ratio. A crown curvature 156 also deviating from the basic pitch angle is provided for the roller element 110. A small amount of pivotal displacement of the roller element 110 about pivot 92 occurs during movement of the roller element 110 between its limit positions for corrective variation in the basic pitch angle from which the roller curvatures 154 and
    156 deviate. The curvatures 154 and 156 are theoretically tangent to each other at the contact zone between the roller surfaces for all positions of the roller 110 to minimise slippage. Some corrective modification of the curvature 156 may also be necessary to maintain the intersection between the rotational axis of roller 94 and the pitch line at a constant distance from the pivot point of pivot
    92 in order to minimise normal spin moment of traction. Such error compensation will result in some variation in the contact zone area between the engaging roller elements to affect the contact pressure for any given contact force exerted by the tension device 152 at the variable leverage aforementioned. The resultant contact pressure, dependent on such vari ables as the contact force, the contact zone area, the roller curvatures and the leverage ratio will vary as a function of the displacement of the roller 110 as depicted by curve 174 in Figure 6. As shown, this resultant pressure curve 174 also has a minimum peak at the neutral position of the roller 110.
    WHAT WE CLAIM IS: 1. A change speed transmission, comprising input and output members, a power transmitting gear arrangement directly drivingly interconnecting said input and output members for establishing a relatively high torque power transmission path therebetween, a biasing gear arrangement directly drivingly connected to the input member and coupled with the power transmitting gear arrangement for establishing the drive ratio through the power transmission path between the input and output members, and a variable traction drive as herein defined directly driven by the input member and coupled with the biasing gear arrangement whereby variation of the variable traction drive in use of the transmission will control the torque biasing arrangement to vary said drive ratio, means being provided for varying the contact force between the traction roller and the driven roller of the variable traction drive in accordance with the torque being transmitted through the power transmitting gear arrangement.
  2. 2. A transmission according to claim 1, wherein said traction drive further includes a driven roller in engagement with the traction roller which is rotatable about a fixed axis common to the input and output members,
    and means mounting the driven roller for rotation about a movable axis generally inclined to said fixed axis, and means for displacing the driven roller along said movable axis to vary the drive ratio.
  3. 3. A transmission according to claim 2, wherein said rollers have engaging surfaces characterised by curvatures that deviate from a pitch line generally parallel with said in dined axis to maintain optimum contact pressures for all positions of the drive roller.
  4. 4. A transmission according to claim 2 or 3, wherein said drive ratio is varied as a linear function of the displacement of the driven roller.
  5. 5. A transmission according to claim 2, 3 or 4, wherein said traction drive further includes tension control means for exerting a contact force on one of the rollers at a variable leverage ratio.
  6. 6. A transmission according to claim 1, wherein said traction drive has one of the engaging rollers mounted for rotation about a fixed axis and the other of the rollers mounted for rotation about a pivotally displaceable axis, means being provided for displacing said other roller along said displaceable axis to vary the drive ratio.
  7. 7. A transmission according to any preceding claim, wherein the torque biasing gear means comprises a reduction drive planetary gear set having input elements respectively driven by the input member and the traction drive, and an output carrier element connected to the power transmitting gear arrangement.
  8. 8. A transmission according to claim 7, wherein the power transmitting gear arrangement comprises a differential gear set having an input element connected to the input member, a planet carrier connected to the output element of the torque biasing gear means and an output element, and a power combining gear set drivingly connecting the carrier and output element of the differential gear set to the output member.
  9. 9. A change speed transmission constructed and arranged to operate substantially as hereinbefore described with reference to the accompanying drawings.
GB12566/78A 1977-04-14 1978-03-30 Traction controlled in-line transmission Expired GB1599953A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US05/787,372 US4192201A (en) 1976-08-20 1977-04-14 Traction controlled in-line transmission

Publications (1)

Publication Number Publication Date
GB1599953A true GB1599953A (en) 1981-10-07

Family

ID=25141270

Family Applications (1)

Application Number Title Priority Date Filing Date
GB12566/78A Expired GB1599953A (en) 1977-04-14 1978-03-30 Traction controlled in-line transmission

Country Status (8)

Country Link
JP (1) JPS53129766A (en)
AU (1) AU517774B2 (en)
CA (1) CA1077305A (en)
DE (1) DE2815322A1 (en)
FR (1) FR2387387A1 (en)
GB (1) GB1599953A (en)
NL (1) NL7803812A (en)
SE (1) SE7804209L (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007052217A1 (en) * 2005-11-02 2007-05-10 Graziano Trasmissioni S.P.A. Continuously-variable-ratio transmission

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB169463A (en) * 1920-09-24 1922-04-20 Gaston Castel De Courval Variable-speed and reversing gearing suitable for motor-vehicles
US3820416A (en) * 1973-01-05 1974-06-28 Excelermatic Variable ratio rotary motion transmitting device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007052217A1 (en) * 2005-11-02 2007-05-10 Graziano Trasmissioni S.P.A. Continuously-variable-ratio transmission

Also Published As

Publication number Publication date
NL7803812A (en) 1978-10-17
JPS53129766A (en) 1978-11-13
AU3484078A (en) 1979-10-11
FR2387387A1 (en) 1978-11-10
SE7804209L (en) 1978-10-15
AU517774B2 (en) 1981-08-27
DE2815322A1 (en) 1978-10-19
CA1077305A (en) 1980-05-13

Similar Documents

Publication Publication Date Title
US4735598A (en) Continuously variable V-belt transmission
US4297918A (en) Control systems for steplessly-variable ratio transmissions
US6251039B1 (en) Torodial continuous variable transmission
EP2113056B1 (en) Continuously variable transmission
CA1109294A (en) Transmission-differential combination
US4192201A (en) Traction controlled in-line transmission
US4624153A (en) Continuously variable transmission
US4098146A (en) Traction-drive transmission
US4125037A (en) Variable speed transmission means
GB2100372A (en) Improvements in or relating to steplessly-variable ratio transmissions
US5512021A (en) Variable ratio transmission
EP0416492B1 (en) Continuous speed-shifting device
GB2023753A (en) Improvements in or relating to control systems for steplessly variable ratio transmission
US3046814A (en) Power transmission
US20140349800A1 (en) Continuously variable transmission (cvt) device controlled by a geared motor
GB2054774A (en) Steplessly variable epicyclic gearing
US5876299A (en) Infinitely variable speed transmission
US4192200A (en) Variable ratio gear transmission
GB2160598A (en) Self regulating transmission
WO2004063598A1 (en) Continuously adjustable gear
GB1599953A (en) Traction controlled in-line transmission
US4304154A (en) Variable ratio transmission mechanism
EP2122201B1 (en) Twin variator transmission arrangement
US4392395A (en) Infinitely variable transmission
JPH07117133B2 (en) V-belt type continuously variable transmission

Legal Events

Date Code Title Description
PS Patent sealed
PCNP Patent ceased through non-payment of renewal fee