CA1108888A - Stepless change-speed apparatus - Google Patents
Stepless change-speed apparatusInfo
- Publication number
- CA1108888A CA1108888A CA341,189A CA341189A CA1108888A CA 1108888 A CA1108888 A CA 1108888A CA 341189 A CA341189 A CA 341189A CA 1108888 A CA1108888 A CA 1108888A
- Authority
- CA
- Canada
- Prior art keywords
- driving
- driven
- frictional
- bevel gear
- driving rotation
- 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
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
- 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
- F16H15/08—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 is a disc with a flat or approximately flat friction surface
- F16H15/10—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 is a disc with a flat or approximately flat friction surface in which the axes of the two members cross or intersect
- F16H15/12—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 is a disc with a flat or approximately flat friction surface in which the axes of the two members cross or intersect in which one or each member is duplicated, e.g. for obtaining better transmission, for lessening the reaction forces on the bearings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Friction Gearing (AREA)
- Transmission Devices (AREA)
- Structure Of Transmissions (AREA)
- Transmissions By Endless Flexible Members (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
The invention provides a speed change apparatus which can give step-lessly variable output rotation speed by causing displacement of a driven rotation member to alter frictional engagement positions on a plurality of driving rotation members kept in such frictional transmission engagement with the driven rotation member. Smooth and reliable driving power transmission is guaranteed in this manner.
The invention provides a speed change apparatus which can give step-lessly variable output rotation speed by causing displacement of a driven rotation member to alter frictional engagement positions on a plurality of driving rotation members kept in such frictional transmission engagement with the driven rotation member. Smooth and reliable driving power transmission is guaranteed in this manner.
Description
This invention relates to a speed-change appara-tus adapted to give s-teplessly variable output rotation speed by causing displacement of driven rotation member means -to alter frictional engagement positions with respect to driving rota-tion member means kept in fric-tional transmission engagement : therewith.
Conventional s-tepless speed change apparatus of this type has a single driving rotation member in frictional engage-ment with a driven rota-tion member.
With such conventional apparatus, secure driving power transmission cannot be attained unless the driving and driven .
rotation members are urged together under considerable force ; owing to -the fact -that both oE the members are in fric-tion engagement wi-th each other only at a sinyle contact spo-t. Mow-cver, the use of such a strong Eorce results in the drawback of causing heavier abrasion of both of the engaging members. Such a strong compression force exerted on a single contact spot in the intention of attaining sufficient driving power transmission causes further difficulty also in that a large unbalanced bending load is exerted on the shaft of the driven rotation member in one direction, which ultimately results in -the failure to attain smooth transmission of the driving power.
The main object of tiliS invention is to provide a step-less speed change apparatus that avoids the difficulties of the ; conventional construc-tion as above and which will reliably and smoothly transmit sufficient driving power.
Another object of this invention is to provide a step-less speed change apparatus of the type mentioned above which has a simple structure.
~ccordingly, the present invention provides a stepless speed change apparatus, comprising: a driving bevel gear for engine power transmission, a plurality of driven bevel gears each in meshing engagement with -the driving bevel grear and hav-ing their rotation axes intersecting at a point, respective driv-ing rotation members provided for each driven bevel gear and arranged -to be rotatable integrally -therewith but axially movable relative thereto, said driving ro-tation memhers each having a frictional transmission surface, an output shaft journaled to extend coaxially with the driving bevel gea:r and lie on an ex-ten-sion ofthe axisthereof, adriven rotationmember splinedon theoutput shaft having a frictionalperipheral surfacethereof in power trans-mission engagement with the frictional transmission surfaces ofthe driving rotation members, whereby the fric-tional engagement positions on the driving frictional transmission surfaces may be altered, and means for urging the driving rota-tion members to bear on the driven rotation member.
Ow.i.ny to the provision of such a plurali.ty of drivi.ng rotation members which are kept in power transmission engagement with a driven rotation member, the driving power allo-ted to and borne by each of the transm:ission engagement spots of reduced, which in turn reduces the abrasion and accordingly the transmis-sion power loss in the stepless speed changing.
At the same time, power transmission realized at such a plurality of separate engagement spots of the driven rotation member contributes to better balanc:ing in -the power -transmission, namely -the heavy unbalanced bending load exerted on the shaft of the driven rotation member in one direction is reduced when com-pared with the conventional structure in which the power trans-mission occurs at a single engagement spot. It has thus been made possible to realize smooth transmission.
~ ividing the driving power into such plurality of trans-mission lines being realized by providing the corresponding numberof driven bevel gears, each meshing with a common driving bevel gear. The structure is quite simple and compact.
:
Still another object oE this invention is to make the frictional driving power transmission from -the clriv:ing rotation members to the driven rotation member more reliable.
In order to attain this object, cam mechanisms are provided which are adapted to cause, as the driven bevel gears are rotated, the driving rotation members -Io be urged on to the driven rotation member with the urging force proportional to -the driving torque.
The invention will now be described in more de-tail by ~ 10 way of example only, with reference to -the accompanying drawings ; in which:
Fig. 1 is a longitudinal vertical sectional view of a transmission section of a trac-tor, with some non-relevant parts om;-ttec1 Eor clarity;
Fig. 2 is an en:Larged view of a portion essential -to the understandiny of the invention;
Fig. 3 is a view taken as on line III-III in Fig. 2, and Fig. 4 is a view similar to Fig. 3 but of a modified embodiment of the invention.
In the transmission section of a tractor shown in the accompanying drawincJs, the driving power frorn an engine E is transmitted, via a main clutch 1, to a main shaft 2 and further transmitted, via a main speed-change apparatus 3 and a planetary gearing reduction mechanism 4 to a sleeve shaft 5. It is sup-posed that the driving power is still to be transmi-t-ted from the sleeve shaft 5 normally via an auxiliary speed-change apparatus (not illus-trated) to a sleeve transmission shaft 6. From this sleeve transmission shaft 6 after the auxiliary change-speed apparatus, the driving power is transmitted on the one hand to rear-wheel axles (not illustrated) via a differential mechanism - (not illustrated) and on the o-ther hand tc front-wheel axles (~lOt ~ 3~
illustrated) via a transmission shaft 8 journalled in the lower-most portion of -the overall -transmission case 7.
It is further supposed that the main shaft 2 extends -to the rear of the transmission case 7, though not illustrated, to transmit the driving power from the rear end thereof normally via another speed-change apparatus to a power-take-off shaEt.
Designa-ted at 9 in Fig. 1 is a hydraulic pump to drive a lift-arm-driving cylinder (not illustrated), wi-th gear oil in the transmission case 7 serving as the hydraulic medium.
Looking now in detail in-to the main speed-change appara-tus 3 with reference to F`igs. 2 and 3, the driving power is trans-mitted frolrl-the main shaf-t 2 to an input shaEt 11 and Eurther transmitted via a driving k~eve:L gear 13 to three drivell bevel gears 12a, 12b, 12c disposed in such a manner that the axes thereof cross together at a point. With these driven bevel gears 12a, 12b, 12c there are associated -the respective driving rota-tion members 14a, 14b, 14c, for free rotation and axial sliding, relative to the bevel gears, with their rotating edge surfaces F
adapted for frictional transmission engagemen-t. Within the space def:ined by -thcse three driving rotation members 14a, 14b, :L4c arranged generally in a gate Eorrn, there is journaled an ou-tput shaft 15 to extend coaxiallv with the driving bevel gear 13, thus on the extension of one and the same axis common thereto, with a driven rotation member 16 splined on the output shaft 15, having frictional peripheral surface thereof adapted to be in power transmission engagement with the mating fric-tional -transmission surEaces F of the driving rotation members 14a, 14b, 14c with possibility of altering the frictional engagement positions on the frictional transmission surfaces F in the respec-tive radial directions thereof.
Referring particularly to the driving rotation member 14a, it will be seen that in the rota-ting edge surface thereof on the side opposite to the said Erictional transmission surface F
and in the rotating edge surface opposed thereto of -the driven bevel gear 12a there are formed alignable pairs of depressions 17 and 18, respectively, preferably in three or more yairs, with a ball 19 fit-ted in each cavity of the aligned depression pair 17, 18. The depression 17 on the side of the drivinc~ rotation member 14a is made -to be conical in shape to receive biasing means constructed as a ball-cam mechanism 20. This urges the driving rotation member 14a to forcibly bear on to the driven rotation member 16 as the driven bevel gear 12a is rotated. With this camming function, the force urging the driving rotation member 14a to forcibly bear on to the driven rota-tion member 16 set in a desired adjustment pos:ition is proportlonal to the clrivlng torque of the driving rotation mernber 14a, thus realizing a stronger compression force at -the higher torque and thereby achieving reliable transmission of the driving power.
Although the ball-cam mechanism 20 has been described with reference only to the specific one driving rota-tion member 14a and the mating driven bevel gear 12a, similar ball-cam mech-anisms 20 are provided for each pair of o-ther driving rotation members 14b, 14c and the driven bevel gears 12b, 12c. With such a construction, it is possible to transmit -the driving power from -the driven bevel gears 12a, 12b, 12c to the output shaft 15 in a stepless speed-changing manner utilizing the peripheral speed difference at the adjustably selected different radial positions on the driving rotation members 14a, 14b, 14c. As is apparent, each depression 17 may also be elongate in the peripheral direc tion, rather than the conical shape as already mentioned, result-ing in substantially the same effect.
Designated in the illus-tration at 21 are compression springs respectively for urging the driving ro~ation members l~a, 14b, l~c to always make contact with the driven rotation member 16.
:
Fig. 4 shows the three pairs of the driven bevel gears 12a, 12b, 12c and the driving rotation members 14a, 14b, 14c dis posed in a modified arrangement. More particularly, the rotation axes of these three pairs are here spaced one from another a-t an angular interval larger than a right angle, thereby having the driving rotation members 14a, 14b, 14c serve to fixedly position or securely set the driven rotation member 16 and also to suppress the fluctuating movement of the axis thereof as it is rotated.
It should be noted that -the cam mechanism 20 is not - 10 limited to a ball-cam as in the embodiment specifically described . hereinabove, but may be modified. For instance, integral lug portions may be provided on either part of the driven bevel gear 12a, 12b, 12c or the driving rotation member 14a, 14b, 14c and adapted to be :Eitted in respective depressions of the matirlg other part. rrhis leads to a camming action similar to that des-cribed hereinabove.
The described embodiments are of course not limited to use ln a tractor. For example, they may be employed as auxiliary speed-change apparatus.
:;
'
Conventional s-tepless speed change apparatus of this type has a single driving rotation member in frictional engage-ment with a driven rota-tion member.
With such conventional apparatus, secure driving power transmission cannot be attained unless the driving and driven .
rotation members are urged together under considerable force ; owing to -the fact -that both oE the members are in fric-tion engagement wi-th each other only at a sinyle contact spo-t. Mow-cver, the use of such a strong Eorce results in the drawback of causing heavier abrasion of both of the engaging members. Such a strong compression force exerted on a single contact spot in the intention of attaining sufficient driving power transmission causes further difficulty also in that a large unbalanced bending load is exerted on the shaft of the driven rotation member in one direction, which ultimately results in -the failure to attain smooth transmission of the driving power.
The main object of tiliS invention is to provide a step-less speed change apparatus that avoids the difficulties of the ; conventional construc-tion as above and which will reliably and smoothly transmit sufficient driving power.
Another object of this invention is to provide a step-less speed change apparatus of the type mentioned above which has a simple structure.
~ccordingly, the present invention provides a stepless speed change apparatus, comprising: a driving bevel gear for engine power transmission, a plurality of driven bevel gears each in meshing engagement with -the driving bevel grear and hav-ing their rotation axes intersecting at a point, respective driv-ing rotation members provided for each driven bevel gear and arranged -to be rotatable integrally -therewith but axially movable relative thereto, said driving ro-tation memhers each having a frictional transmission surface, an output shaft journaled to extend coaxially with the driving bevel gea:r and lie on an ex-ten-sion ofthe axisthereof, adriven rotationmember splinedon theoutput shaft having a frictionalperipheral surfacethereof in power trans-mission engagement with the frictional transmission surfaces ofthe driving rotation members, whereby the fric-tional engagement positions on the driving frictional transmission surfaces may be altered, and means for urging the driving rota-tion members to bear on the driven rotation member.
Ow.i.ny to the provision of such a plurali.ty of drivi.ng rotation members which are kept in power transmission engagement with a driven rotation member, the driving power allo-ted to and borne by each of the transm:ission engagement spots of reduced, which in turn reduces the abrasion and accordingly the transmis-sion power loss in the stepless speed changing.
At the same time, power transmission realized at such a plurality of separate engagement spots of the driven rotation member contributes to better balanc:ing in -the power -transmission, namely -the heavy unbalanced bending load exerted on the shaft of the driven rotation member in one direction is reduced when com-pared with the conventional structure in which the power trans-mission occurs at a single engagement spot. It has thus been made possible to realize smooth transmission.
~ ividing the driving power into such plurality of trans-mission lines being realized by providing the corresponding numberof driven bevel gears, each meshing with a common driving bevel gear. The structure is quite simple and compact.
:
Still another object oE this invention is to make the frictional driving power transmission from -the clriv:ing rotation members to the driven rotation member more reliable.
In order to attain this object, cam mechanisms are provided which are adapted to cause, as the driven bevel gears are rotated, the driving rotation members -Io be urged on to the driven rotation member with the urging force proportional to -the driving torque.
The invention will now be described in more de-tail by ~ 10 way of example only, with reference to -the accompanying drawings ; in which:
Fig. 1 is a longitudinal vertical sectional view of a transmission section of a trac-tor, with some non-relevant parts om;-ttec1 Eor clarity;
Fig. 2 is an en:Larged view of a portion essential -to the understandiny of the invention;
Fig. 3 is a view taken as on line III-III in Fig. 2, and Fig. 4 is a view similar to Fig. 3 but of a modified embodiment of the invention.
In the transmission section of a tractor shown in the accompanying drawincJs, the driving power frorn an engine E is transmitted, via a main clutch 1, to a main shaft 2 and further transmitted, via a main speed-change apparatus 3 and a planetary gearing reduction mechanism 4 to a sleeve shaft 5. It is sup-posed that the driving power is still to be transmi-t-ted from the sleeve shaft 5 normally via an auxiliary speed-change apparatus (not illus-trated) to a sleeve transmission shaft 6. From this sleeve transmission shaft 6 after the auxiliary change-speed apparatus, the driving power is transmitted on the one hand to rear-wheel axles (not illustrated) via a differential mechanism - (not illustrated) and on the o-ther hand tc front-wheel axles (~lOt ~ 3~
illustrated) via a transmission shaft 8 journalled in the lower-most portion of -the overall -transmission case 7.
It is further supposed that the main shaft 2 extends -to the rear of the transmission case 7, though not illustrated, to transmit the driving power from the rear end thereof normally via another speed-change apparatus to a power-take-off shaEt.
Designa-ted at 9 in Fig. 1 is a hydraulic pump to drive a lift-arm-driving cylinder (not illustrated), wi-th gear oil in the transmission case 7 serving as the hydraulic medium.
Looking now in detail in-to the main speed-change appara-tus 3 with reference to F`igs. 2 and 3, the driving power is trans-mitted frolrl-the main shaf-t 2 to an input shaEt 11 and Eurther transmitted via a driving k~eve:L gear 13 to three drivell bevel gears 12a, 12b, 12c disposed in such a manner that the axes thereof cross together at a point. With these driven bevel gears 12a, 12b, 12c there are associated -the respective driving rota-tion members 14a, 14b, 14c, for free rotation and axial sliding, relative to the bevel gears, with their rotating edge surfaces F
adapted for frictional transmission engagemen-t. Within the space def:ined by -thcse three driving rotation members 14a, 14b, :L4c arranged generally in a gate Eorrn, there is journaled an ou-tput shaft 15 to extend coaxiallv with the driving bevel gear 13, thus on the extension of one and the same axis common thereto, with a driven rotation member 16 splined on the output shaft 15, having frictional peripheral surface thereof adapted to be in power transmission engagement with the mating fric-tional -transmission surEaces F of the driving rotation members 14a, 14b, 14c with possibility of altering the frictional engagement positions on the frictional transmission surfaces F in the respec-tive radial directions thereof.
Referring particularly to the driving rotation member 14a, it will be seen that in the rota-ting edge surface thereof on the side opposite to the said Erictional transmission surface F
and in the rotating edge surface opposed thereto of -the driven bevel gear 12a there are formed alignable pairs of depressions 17 and 18, respectively, preferably in three or more yairs, with a ball 19 fit-ted in each cavity of the aligned depression pair 17, 18. The depression 17 on the side of the drivinc~ rotation member 14a is made -to be conical in shape to receive biasing means constructed as a ball-cam mechanism 20. This urges the driving rotation member 14a to forcibly bear on to the driven rotation member 16 as the driven bevel gear 12a is rotated. With this camming function, the force urging the driving rotation member 14a to forcibly bear on to the driven rota-tion member 16 set in a desired adjustment pos:ition is proportlonal to the clrivlng torque of the driving rotation mernber 14a, thus realizing a stronger compression force at -the higher torque and thereby achieving reliable transmission of the driving power.
Although the ball-cam mechanism 20 has been described with reference only to the specific one driving rota-tion member 14a and the mating driven bevel gear 12a, similar ball-cam mech-anisms 20 are provided for each pair of o-ther driving rotation members 14b, 14c and the driven bevel gears 12b, 12c. With such a construction, it is possible to transmit -the driving power from -the driven bevel gears 12a, 12b, 12c to the output shaft 15 in a stepless speed-changing manner utilizing the peripheral speed difference at the adjustably selected different radial positions on the driving rotation members 14a, 14b, 14c. As is apparent, each depression 17 may also be elongate in the peripheral direc tion, rather than the conical shape as already mentioned, result-ing in substantially the same effect.
Designated in the illus-tration at 21 are compression springs respectively for urging the driving ro~ation members l~a, 14b, l~c to always make contact with the driven rotation member 16.
:
Fig. 4 shows the three pairs of the driven bevel gears 12a, 12b, 12c and the driving rotation members 14a, 14b, 14c dis posed in a modified arrangement. More particularly, the rotation axes of these three pairs are here spaced one from another a-t an angular interval larger than a right angle, thereby having the driving rotation members 14a, 14b, 14c serve to fixedly position or securely set the driven rotation member 16 and also to suppress the fluctuating movement of the axis thereof as it is rotated.
It should be noted that -the cam mechanism 20 is not - 10 limited to a ball-cam as in the embodiment specifically described . hereinabove, but may be modified. For instance, integral lug portions may be provided on either part of the driven bevel gear 12a, 12b, 12c or the driving rotation member 14a, 14b, 14c and adapted to be :Eitted in respective depressions of the matirlg other part. rrhis leads to a camming action similar to that des-cribed hereinabove.
The described embodiments are of course not limited to use ln a tractor. For example, they may be employed as auxiliary speed-change apparatus.
:;
'
Claims (6)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A stepless speed change apparatus, comprising a driv-ing bevel gear for engine power transmission, a plurality of driven bevel gears, each in meshing engagement with the driving bevel gear and having their rotation axes intersecting at a point, respective driving rotation members provided for each driven bevel gear and arranged to be rotatable integrally therewith but axially movable relative thereto said driving rotation members each having a frictional transmission surface, an output shaft jour-naled to extend coaxially with the driving bevel gear and lie on an extension of the axis thereof, a driven rotation member splined on the output shaft, having a frictional peripheral surface there-of in power transmission engagement with the frictional trans-mission surfaces of the driving rotation members, whereby the frictional engagement positions on the driving frictional trans-mission surfaces may be altered, and means for urging the driving rotation members to bear on the driven rotation member.
2. An apparatus as claimed in claim 1, comprising three pairs of said driven bevel gears and said driving rotation members said three pairs being arranged generally so as to be equally spaced in the circumferential direction around the driven rota-tion member.
3. An apparatus as claimed in claim 2, wherein said urging means comprise respective cam mechanisms interposed bet-ween each pair of the driving rotation member and the driven bevel gear, the cam mechanisms being adapted to cause, as the driven bevel gears are rotated, the driving rotation members to thereby be urged along the respective axes thereof on to the driven rotation member.
4. An apparatus as claimed in claim 3, wherein the cam mechanisms are constructed as ball-cams.
5. An apparatus as claimed in claim 2, wherein the three pairs of the driven bevel gears and the driving rotation members are arranged at obtuse angular intervals between the rotation axes thereof.
6. An apparatus as claimed in claim 4 or 5, the appara-tus incorporated in a tractor as the main speed change apparatus therefor.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15824878A JPS5582846A (en) | 1978-12-18 | 1978-12-18 | Speed change gear |
| JP158248/1978 | 1978-12-18 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1108888A true CA1108888A (en) | 1981-09-15 |
Family
ID=15667481
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA341,189A Expired CA1108888A (en) | 1978-12-18 | 1979-12-04 | Stepless change-speed apparatus |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPS5582846A (en) |
| CA (1) | CA1108888A (en) |
| DE (1) | DE2950208C2 (en) |
| FR (1) | FR2444859A1 (en) |
| GB (1) | GB2038430B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5635849A (en) * | 1979-08-30 | 1981-04-08 | Kubota Ltd | Variable speed gear for tractor |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR374843A (en) * | 1907-02-19 | 1907-06-24 | Hilmar Von Minnigerode | Adjustable friction control |
| GB117465A (en) * | 1917-01-13 | 1918-07-15 | Herbert Biggleston | Improvements in Variable Speed Gears. |
| FR604110A (en) * | 1924-10-04 | 1926-04-29 | Friction shifting | |
| GB310064A (en) * | 1927-10-21 | 1929-04-22 | John Standen Shaw | Improvements in speed varying and reversing gear |
| FR908279A (en) * | 1944-12-15 | 1946-04-04 | Gear reducer, servo-variable | |
| US2520057A (en) * | 1947-07-03 | 1950-08-22 | C E Dominguez | Variable speed power transmission |
| FR1013918A (en) * | 1950-03-08 | 1952-08-06 | Improvements to variable speed drives | |
| US3204476A (en) * | 1960-04-05 | 1965-09-07 | William S Rouverol | Variable speed transmission |
| US3108480A (en) * | 1960-11-14 | 1963-10-29 | Kiuchi Yahei | Universal speed converter |
| US3264890A (en) * | 1960-11-28 | 1966-08-09 | Richard T Erban | Variable speed transmission |
| FR1349261A (en) * | 1962-11-08 | 1964-01-17 | Improvements to variable speed friction devices | |
| DE2207033A1 (en) * | 1972-02-15 | 1973-08-23 | Helmut Koerner | CONTINUOUSLY ADJUSTABLE REVERSING GEAR |
| NZ183624A (en) * | 1976-04-10 | 1980-05-08 | Kubota Ltd | Stepless speed change system connected to an internal gear which meshes with a planetary gear system |
-
1978
- 1978-12-18 JP JP15824878A patent/JPS5582846A/en active Pending
-
1979
- 1979-09-13 FR FR7922917A patent/FR2444859A1/en active Granted
- 1979-09-28 GB GB7933754A patent/GB2038430B/en not_active Expired
- 1979-12-04 CA CA341,189A patent/CA1108888A/en not_active Expired
- 1979-12-13 DE DE19792950208 patent/DE2950208C2/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| DE2950208C2 (en) | 1983-04-21 |
| FR2444859A1 (en) | 1980-07-18 |
| FR2444859B1 (en) | 1984-03-09 |
| JPS5582846A (en) | 1980-06-21 |
| GB2038430B (en) | 1983-05-11 |
| DE2950208A1 (en) | 1980-07-03 |
| GB2038430A (en) | 1980-07-23 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |