WO1988009450A1 - Automatic transmission - Google Patents
Automatic transmission Download PDFInfo
- Publication number
- WO1988009450A1 WO1988009450A1 PCT/NO1988/000047 NO8800047W WO8809450A1 WO 1988009450 A1 WO1988009450 A1 WO 1988009450A1 NO 8800047 W NO8800047 W NO 8800047W WO 8809450 A1 WO8809450 A1 WO 8809450A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- driving wheel
- wheel means
- input shaft
- gear
- automatic transmission
- Prior art date
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 47
- 230000008878 coupling Effects 0.000 claims abstract description 20
- 238000010168 coupling process Methods 0.000 claims abstract description 20
- 238000005859 coupling reaction Methods 0.000 claims abstract description 20
- 230000000295 complement effect Effects 0.000 claims abstract description 5
- 230000001419 dependent effect Effects 0.000 claims abstract description 5
- 238000003825 pressing Methods 0.000 claims description 4
- 238000010586 diagram Methods 0.000 description 3
- 241000446313 Lamella Species 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 150000002500 ions Chemical class 0.000 description 2
- 239000004809 Teflon Substances 0.000 description 1
- 229920006362 Teflon® Polymers 0.000 description 1
- 230000003213 activating effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/14—Inputs being a function of torque or torque demand
- F16H59/16—Dynamometric measurement of torque
-
- 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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
-
- 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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/10—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with one or more one-way clutches as an essential feature
Definitions
- the present invention relates to an automatic transmission which will shift only dependent on the torque in the input shaft and the output shaft with said shafts always being interconnected via drive wheel means.
- Automatic transmissions are known and widely used in private cars, trucks and motor coaches, etc.
- a fluid torque converter and a transmission is a hydraulic system for controlling and activating various transmission functions included.
- Such transmissions are operated by dependence on the speed of rotation of one transmission shaft as well as throttle opening.
- Automatic V-belt transmissions with variable pulleys are also known.
- the automatic transmission according to the invention is a simple construction achieved, the structure of which is much similar to that of conventional manual standard transmiss ⁇ ions.
- the present concept is a higher shifting level from high to low than from low to high achieved, which entails that the high gear is engaged as long as possible and the low gear is engaged not more than strictly necessary.
- the present concept also has the pre-eminence that the shifting level may be set or adjusted by the user.
- the input shaft comprises a portion provided with external thread means on which a first driving wheel means having complementary internal thread means is running in such a way that said first driving wheel means is slightly axially moveable in relation to said input shaft along said threaded portions, and that a second axially sliding and freely rotatable driving wheel means is mounted on the input shaft for releasable engaging a ring wheel fixed to said input sha t as a coupling means, and that a third free wheeled driving wheel is supported on said output shaft, said third driving wheel means being constantly in mesh with said first driving wheel means, and that a fourth driving wheel means is fixed to the output shaft and is constantly in mesh with said second driving wheel means, and means urging said first driving wheel means axially towards and into engagement with said second driving wheel means.
- Fig. 1 is a diagrammatical view of a first embodiment of the transmission according to the invention
- Fig. 2 is a diagrammatical view of two transmissions which are connected in series in order to increase the number of gear ratios
- Fig. 3 is a diagrammatical view of a second embodiment of the transmission according to the invention
- Fig. 4 is a diagrammatical view of a variant of the second embodiment of the invention
- Fig. 5 is a diagrammatical view of another variant of the second embodiment according to the invention
- Fig. 6 is a diagrammatical view of a third embodiment of the present invention
- Fig. 7 is a diagrammatical view of the first embodiment of the transmission according to the invention in a high gear
- Fig. 8 is a diagrammatical view of the first embodiment of the transmission according to the invention in a low gear
- Fig. 9 is a torque diagram of the shift between high and low, and between low and high.
- FIG. 1 is a diagrammatical view of an automatic transmission 15 having two shifting steps (two-speed).
- An input shaft 10 is supported in a surrounding case 5, and similarly is an output shaft 11 supported in the case 5.
- the shaft 10 has an externally threaded portion 9 preferably of a steep pitch angle, e.g. of the kind used in Bendix-drives.
- a first gear 1 having complementary internal threads is mounted on said shaft portion and is slightly axially moveable along the threaded sections.
- the gear 1 has external teeth which may be straight cut, but are preferably helical gears.
- a spring 7, preferably a coil spring, is provided between the gear 1 and a spring seat 6.
- the seat or disc 6 has internal threads cooperating with corresponding threads on the shaft 10.
- the spring 7 can be tensioned and relieved, respectively, by turning the disc 6.
- a second sliding gear 2 is mounted on input shaft 10 and thus is able to slight movements in an axial direction.
- the gear 2 is also freely rotatable on shaft 10.
- a ring wheel 8 is fixedly connected to input shaft 10.
- the illustrated clearances between the first gear 1 and the second gear 2, and between the second gear 2 and the ring wheel 8 are in fact very small in a true construction.
- the first gear 1 is meshed with a third gear 3 which is supported on output shaft 11 via a sprag or free wheel clutch means 13.
- the free wheel 13 causes the third gear 3 to turn freely in one direction relative to the shaft 11, and locks to the shaft upon rotation in the opposite direction.
- a fourth gear 4 is fixed to the output shaft 11 and is meshed with the second gear 2.
- the pairs of gears 1 and 3, and 2 and 4, respectively, are always mutually engaged, but as mentioned the gears 1 and 2 is able to move slightly along the shaft 10 and thus along the gears 3 and 4.
- the gear set 1 and 3 forms a low gear, whereas the gear set 2 and 4 forms a high gear.
- Fig. 2 is a diagrammatical view of an automatic multistep transmission with two equal transmission units 15 and 15' connected In series.
- the transmissions 15 and 15' are constructed as disclosed with respect to fig. 1.
- Such an interconnection will provide a four-step transmission.
- Various shift levels will be determined by dimensioning of the couplings or clutches, the gears and by adjustment of the springs.
- Fig. 3 presents a second embodiment of the automatic transmission 25 according to the invention.
- the input shaft 10 with associated components is constructed- similar to the input shaft shown in fig. 1, except for the first gear 1.
- the gear 1 is designed as a free wheel via a sprag or one-way clutch 13 preventing rotation of the gear in relation to the shaft 10 in one particular direction.
- the shaft is provided with a threaded portion 9, and the gear 1 has corresponding internal threads.
- the output shaft constituded of a surrounding drum 21 provided with internal gears 23, 24 which mesh with the gear 1 and the gear 2, respectively.
- the drum 21 is rotatable in fixed bearings 18 and 18'.
- the input shaft 10 is in turn eccentrically supported in the fixed bearings 18 and 18'.
- Fig. 4 presents a third embodiment 35 of the automatic transmission according to the invention.
- the input shaft 10 corresponds to the input shaft in fig. 3 as regards structure and function.
- this embodiment also comprises a surrounding drum 31 with internal gears 33 and 34.
- intermediate or planetary gears 38 and 39 are provided between the gears 1 and 33 and the gears 2 and 34, respectively.
- Fig. 5 presents an automatic transmission which is a variant of the embodiment shown in fig. 4.
- the input shaft 10 with associated components is similarly constructed to the shaft shown in fig. 4.
- the input shaft 10 is centric supported in the bearings 19 and 19'.
- the surrounding drum 41 with associated internal gears 43 and 44 corresponds substantially to the drum 31 in fig. 4.
- the planetary gears 48 and 49 are slightly larger than the gears 38 and 39, and the gear ratio achieved is thus altered.
- Fig. 6 presents a fourth embodiment Of the automatic transmission 55 according to the invention.
- the input shaft 10 is -provided with a spring seat or disc 6 and a first gear 1 and an intermediate spring 7 therebetween.
- the input shaft 10 is eccentrically supported in bearings 18 and 18'.
- the gear 1 is - as shown in fig. 3,4 and 5 - engaged to the shaft 10 via threads 9 and free wheel clutch means or sprag 13.
- the gear 1 is meshed with the gear 58 which is fixedly connected to a shaft 56 which is, in turn, fixedly connected to a smaller gear 59.
- a multiple lamella clutch 52 is also provided with one set of lamellas or discs engaged to the input shaft 10.
- the other set of discs is engaged to a ring gear 57 which is provided with external teeth engaged with the gear 59.
- Said ring gear 57 is also engaged with a gear 54 internal of the drum 51.
- This preferred embodiment comprises an internal cone or taper in the ring wheel 8 and an external cone provided on the second gear 2. Together said components form a conical coupling or clutch 17.
- the first gear 1 is also able to thrust on the second gear 2.
- both first and second gears can move slightly in an axial direction in relation to the input shaft 10.
- Fig. 7 shows the conical coupling 17 in an engaged position causing power to be transmitted via the gears 2 and 4, I.e. in high gear.
- Fig. 8 presents a transmission 15 corresponding to that in fig. 7, except the power being transmitted via the gear set 1 and 3, i.e. in low gear.
- Fig. 9 presents a torque diagram indicating that shifting from low to high gear will occur at a lower torque than shifting from high to low. This fact will be further described below.
- the spring 7 presses against the gear 1 which is, in turn, pressed towards the second gear 2, which is also axially slidably and freely rotatable supported on the input shaft 10.
- the ring wheel 8 is fixed to the shaft 10, and by means of the spring 7 the second gear 2 is forced into conical engagement with the ring wheel 8 so as to be locked to the ring wheel 8.
- Power is transmitted from the gear 2 to the gear 4 which is fixed to the output shaft 11.
- the first gear 1, however, will have the same rotational speed as the second gear 2.
- the third gear 3 is mounted on the shaft 11 via the one way clutch or sprag 13, so that the gear 3 runs like a free wheel on the shaft 11.
- the gear 3 will rotate at a lower speed than the output shaft 11.
- the spring 7 When the torque demand again decreases the spring 7 will at a certain torque value push the gears 1 and 2 to the left hand side in the fig., i.e. the coupling 17 will reengage.
- the gear 2 is reconnected to the input shaft 10 via the ring wheel 8.
- the rotational speed of the output shaft 11 increases since the power is transmitted via the gear set 2 and 4.
- No power is transmitted to the gear 3 since the output shaft 11 rotates at a higher speed than the gear 3.
- the shifting torque is controlled by the spring 7.
- the transmittable torque is proportional to the spring pressure against the coupling.
- the spring pressure and, thus, the transmittable torque can be adjusted by means of the disc 6, as previously stated. In shifting from high gear to low gear only the transmittable torque via the coupling is decisive.
- gears are helical as in fig. 7 a power component will be created towards the right hand side in the fig. , or against the spring force when driving in low gear.
- gear 1 In low gear operation the gear 1 is further screwed towards the right hand side in the fig. by means of its internal threads. This force also acts against the spring force.
- shifting from low gear will, thus, occur at a lower torque than shifting from high to low.
- the other embodiments except the one shown in fig. 6, operates correspondingly, but the gears and shafts are designed and located in a different way.
- the mode of operation of the automatic transmission 55 as shown in fig. 6 is as follows: In high gear the first gear 1 Is forced towards the coupling 52 by means of the spring 7. The power is transmitted to the ring gear 57 which is meshed with the internal gear 54 in the drum 51. Rotational movement is also transmitted from the ring gear 57 to the transfer gear 59, and further to the intermediate gear 58. The intermediate gear 58 is in turn in mesh with the gear 1 which runs like a free wheel by means of the sprag or clutch 13. In this case (also according to fig.
- the sprag runs on an externally smooth sleeve (not detailed in the drawings) internally provided with the helical threads, which sprag and sleeve are axially retained to the gear 1.
- the transferable torque via the coupling 52 will be exceeded at a certain value.
- the coupling 52 will momentarily slip.
- the rotational speed of the output shaft or drum 51 will immediately be reduced or converged towards the gear 1 until engagement with the shaft 10.
- the power is now transmitted by the gear 1, the inter ⁇ mediate gear 58 via the shaft 56 and to the gear 59 and, further, via the ring gear 57 to the internal gear 54 in the drum 51. Consequently is a transmission with considerably higher shift ratio between high and low gear achieved.
- the coupling 17 not necessarily need to be of the conical or tapered kind, but may be of any
- the driving wheels means not necessarily are gears, but may be belt pulleys, frictional rollers or any kind of means able to transmit torques or power.
- the spring pressing against the first driving wheel means may t5 be any means providing a thrust or bias, e.g. a Belleville spring, hydraulically regulatable pressure, or the like.
- the transmission may be of the type running in an oil bath, or it may be a dry type transmission using plastic and teflon components.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Transmission Devices (AREA)
- Control Of Transmission Device (AREA)
- Vending Machines For Individual Products (AREA)
- Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FI890383A FI890383A0 (en) | 1987-05-27 | 1989-01-26 | AUTOMATISK VAEXEL. |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
NO872225 | 1987-05-27 | ||
NO872225A NO162165C (en) | 1987-05-27 | 1987-05-27 | AUTOMATIC TRANSMISSION. |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1988009450A1 true WO1988009450A1 (en) | 1988-12-01 |
Family
ID=19889976
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/NO1988/000047 WO1988009450A1 (en) | 1987-05-27 | 1988-05-27 | Automatic transmission |
Country Status (6)
Country | Link |
---|---|
EP (1) | EP0321509A1 (en) |
JP (1) | JPH02500767A (en) |
AU (1) | AU1784488A (en) |
FI (1) | FI890383A0 (en) |
NO (1) | NO162165C (en) |
WO (1) | WO1988009450A1 (en) |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0409803A1 (en) * | 1989-07-18 | 1991-01-23 | FIAT AUTO S.p.A. | A gearbox with meshed gears |
EP0508718A1 (en) * | 1991-04-12 | 1992-10-14 | Tai-Her Yang | Automatic transmission |
AU661697B2 (en) * | 1992-07-02 | 1995-08-03 | Tai-Her Yang | An automatic transmission for accommodating variable loads |
EP0632217B1 (en) * | 1993-06-04 | 1997-08-20 | General Motors Corporation | Power transmission and control |
CN1048081C (en) * | 1992-05-13 | 2000-01-05 | 杨泰和 | Coupled gear train for non-harmonic non-equal-ratio complex gear system and application apparatus thereof |
EP0753687B1 (en) * | 1995-07-10 | 2000-05-24 | Ab Volvo | Transmission with helical gears |
WO2012127897A1 (en) * | 2011-03-22 | 2012-09-27 | Denso Corporation | Drive force transmission apparatus |
WO2014000751A1 (en) * | 2012-06-25 | 2014-01-03 | Volvo Lastvagnar Ab | Gear arrangement and dual-clutch transmission provided therewith |
WO2021160946A1 (en) * | 2020-02-13 | 2021-08-19 | Franck Guigan | Transmission with a shaft and dog connected by a thread |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3320397B2 (en) | 2000-03-09 | 2002-09-03 | クラリアント ジャパン 株式会社 | Method of forming reverse tapered resist pattern |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1985662A (en) * | 1931-10-20 | 1934-12-25 | Eclipse Aviat Corp | Transmission |
US2107422A (en) * | 1933-01-26 | 1938-02-08 | George B Moross | Automatic change speed gearing for automotive vehicles |
US2139221A (en) * | 1936-04-24 | 1938-12-06 | Wilhelm B Bronander | Driving mechanism |
DE1775249A1 (en) * | 1968-07-19 | 1971-08-12 | Bosch Gmbh Robert | Stationary gear |
-
1987
- 1987-05-27 NO NO872225A patent/NO162165C/en unknown
-
1988
- 1988-05-27 AU AU17844/88A patent/AU1784488A/en not_active Abandoned
- 1988-05-27 JP JP63504200A patent/JPH02500767A/en active Pending
- 1988-05-27 EP EP88904678A patent/EP0321509A1/en not_active Withdrawn
- 1988-05-27 WO PCT/NO1988/000047 patent/WO1988009450A1/en not_active Application Discontinuation
-
1989
- 1989-01-26 FI FI890383A patent/FI890383A0/en not_active IP Right Cessation
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1985662A (en) * | 1931-10-20 | 1934-12-25 | Eclipse Aviat Corp | Transmission |
US2107422A (en) * | 1933-01-26 | 1938-02-08 | George B Moross | Automatic change speed gearing for automotive vehicles |
US2139221A (en) * | 1936-04-24 | 1938-12-06 | Wilhelm B Bronander | Driving mechanism |
DE1775249A1 (en) * | 1968-07-19 | 1971-08-12 | Bosch Gmbh Robert | Stationary gear |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0409803A1 (en) * | 1989-07-18 | 1991-01-23 | FIAT AUTO S.p.A. | A gearbox with meshed gears |
EP0508718A1 (en) * | 1991-04-12 | 1992-10-14 | Tai-Her Yang | Automatic transmission |
CN1048081C (en) * | 1992-05-13 | 2000-01-05 | 杨泰和 | Coupled gear train for non-harmonic non-equal-ratio complex gear system and application apparatus thereof |
AU661697B2 (en) * | 1992-07-02 | 1995-08-03 | Tai-Her Yang | An automatic transmission for accommodating variable loads |
EP0632217B1 (en) * | 1993-06-04 | 1997-08-20 | General Motors Corporation | Power transmission and control |
EP0753687B1 (en) * | 1995-07-10 | 2000-05-24 | Ab Volvo | Transmission with helical gears |
WO2012127897A1 (en) * | 2011-03-22 | 2012-09-27 | Denso Corporation | Drive force transmission apparatus |
US9334926B2 (en) | 2011-03-22 | 2016-05-10 | Denso Corporation | Drive force transmission apparatus |
WO2014000751A1 (en) * | 2012-06-25 | 2014-01-03 | Volvo Lastvagnar Ab | Gear arrangement and dual-clutch transmission provided therewith |
US9593744B2 (en) | 2012-06-25 | 2017-03-14 | Volve Lastvagnar AB | Gear arrangement and dual-clutch transmission provided therewith |
WO2021160946A1 (en) * | 2020-02-13 | 2021-08-19 | Franck Guigan | Transmission with a shaft and dog connected by a thread |
Also Published As
Publication number | Publication date |
---|---|
NO162165B (en) | 1989-08-07 |
FI890383A (en) | 1989-01-26 |
NO872225D0 (en) | 1987-05-27 |
NO162165C (en) | 1989-11-15 |
FI890383A0 (en) | 1989-01-26 |
AU1784488A (en) | 1988-12-21 |
EP0321509A1 (en) | 1989-06-28 |
NO872225L (en) | 1988-11-28 |
JPH02500767A (en) | 1990-03-15 |
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