WO1987005085A1 - Transmissions a auto-reglage - Google Patents

Transmissions a auto-reglage Download PDF

Info

Publication number
WO1987005085A1
WO1987005085A1 PCT/GB1987/000129 GB8700129W WO8705085A1 WO 1987005085 A1 WO1987005085 A1 WO 1987005085A1 GB 8700129 W GB8700129 W GB 8700129W WO 8705085 A1 WO8705085 A1 WO 8705085A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
rotatable
shaft
output
carrier
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.)
Ceased
Application number
PCT/GB1987/000129
Other languages
English (en)
Inventor
Frederick Michael Stidworthy
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.)
Individual
Original Assignee
Individual
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
Application filed by Individual filed Critical Individual
Publication of WO1987005085A1 publication Critical patent/WO1987005085A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/74—Complexes, not using actuatable speed-changing or regulating members, e.g. with gear ratio determined by free play of frictional or other forces

Definitions

  • THIS INVENTION relates to self-adjusting mechanical transmission devices which find particular, but not exclusive, application in the power train of a motor vehicle.
  • a transmission device comprising an input shaft rotatable about a main axis of rotation, an output shaft, an input gear rotatable with the input shaft, an intermediate rotary assembly mounted for rotation about the main axis and engaged at respective first and second points of engagement at different radial distances from the main axis by first and second gear assemblies driven by the input gear, the first gear assembly transmitting the input torque applied to the input gear to the intermediate assembly in one rotational direction and the second gear assembly transmitting the input torque to the rotatable assembly in the other rotational direction and being coupled to transmit torque to the output shaft.
  • a transmission device embodying the present invention is suitable for use in any situation where the load is of a variable nature or where a load is required to be accelerated to a constant speed from an initial stationary condition.
  • the device is also of use where the power input of a power source during the load is variable or in situations where both the power input and load are variable, either independently of one another or in concert.
  • Figure I is an axial cross-section through a first transmission device embodying the present invention
  • Figure 2 is art oxiol cross-section through ⁇ second transmission device embodying the invention
  • Figure 3 is an axial cross-section through a third transmission device embodying the invention.
  • Figure 4 is an oxial cross-section through a fourth transmission device embodying the invention.
  • Figure 5 is an oxial cross-section through a fifth transmission device
  • Figure 6 is an axial cross-section through a sixth transmission device embodying the invention.
  • FIG. 7 is a diagram for use in explaining in more detail the principle of operation of the sixth embodiment.
  • a first transmission device embodying the invention comprises on input shaft I extending into a casing 2 through an o input journal 3 of the casing and an output shaft 4 extending from casing 2 through an output journal 5.
  • a free-running intermediate shaft 6 is located between the input and output shafts I and 4 by means of locating shaft portions 7 and 8 received in corresponding locating bores in the shafts I and 4.
  • a main carrier 9 is borne by the journals 3 and 5 and the intermediate 5 shaft 6 so as to be independently rotatable about the same main axis X-X as the shafts 1 , 4 and 6.
  • a differential unit of the device comprises a differential carrier 10 which is fixed to or port of the intermediate shaft 6 and presents stub axles 0 1 1 and 12 which are fixed to or part of the carrier 10.
  • First and second layshaft axles 13 and 14 are fixed to or part of the main carrier 9 and support free-running sleeve layshafts 15 and 16 for rotation about respective first and second subsidiary axes Y-Y and Z-Z.
  • a differential input bevel gear 20 having 44 teeth is fixed to or part of input shaft I and engages idler bevel gears 21 and 22 respectively rotatable on stub axles 1 1 and 12 and having 44 teeth each.
  • a differential output bevel gear 23 having 44 teeth engages gears 21 and 22 and is rot ⁇ t ⁇ ble with ⁇ sleeve shaft bearing located on the intermediate shaft 6 and carrying a dif ferential output gear 24 having 47 teeth.
  • Engaged with gear 2k is a planet gf-ar 25 having 47 teeth and rotatable with sleeve shaft 15 which also carries compound planet gear 26 having 36 teeth.
  • Gear 26 is engaged with a static gear 27 having 58 teeth non-rotatably supported by input journal 3 concentrically of the input shaft I .
  • Sun gear 28 having 28 teeth is fixed to or part of intermediate shaft 6 and engages planet gears 29 and 30 having 28 teeth each and rotatable with respective planet laysh ⁇ fts 31 and 32 rotatably carried by a carrier gear 33 having an external gear face 34 provided with 123 teeth.
  • the gear 33 could be a single component as shown or two separate components coupled together for rotation together.
  • Compound planet gears 35 and 36 having 33 teeth each are also rotatable with the layshafts 31 and 32 respectively and engage an output sun gear 37 which is fixed to or part of output shaft 2 and has 23 teeth.
  • the gear face 34 of carrier gear 33 is engaged with a planet gear 38 having 1 23 teeth and rotatable with sleeve shaft 16 which also carries a compound, planet gear 39 having 54 teeth and engaged with a second static gear 40 having 87 teeth and non-rotatably carried by the output journal 5 concentrically of output shaft 2.
  • gear 23 As gear 23 is compounded with gear 24, the latter gear is also provided with a IT rearward torque loading and this is transmitted to the gear 25 with which gear 24 is engaged. Gear 25 transmits this torque to gear 26 which is connected to gear 25 by sleeve shaft 15.
  • gear 25 transmits this torque to gear 26 which is connected to gear 25 by sleeve shaft 15.
  • the 2T torque output from the differential carrier 10 is transmitted along the intermediate shaft 6 to the sun gear 28, thereby providing the sun gear 28 with 2T of torque in the forward direction.
  • the torque of 2T introduced to the output unit is in the forward direction and therefore, as sun gear 28 is engaged with planet gears 29 and 30 at a ratio of I : I , the 2T is applied to gears 29 and 30.
  • the planets 29 and 30 are of course caused to rotate in an opposite direction to gear 28 at 2T and transmit this rotation to compound planet gears 35 and 36 via layshaf ts 31 and 32.
  • gears 35 and 36 have 33 teeth each and output gear 37 has 23 teeth, the ratio at which the 2T is transferred to gear 37 is 23 - 33, i.e. 0.6969697 : I . Therefore, the 2T from provides only I .393994T in the forward direction for the output gear 37, the difference between this and 2T, namely 0.6060606T, being applied to the carrier gear 33 in the forward direction.
  • gears 35 and 36 would simply progress or walk forwardly around the loaded output gear 37.
  • gear 33 is engaged at a ratio of I : I with planet gear 38, so that the 0.60606 06T is transferred to gear 38 causing it to rotate in the rearward direction.
  • the main carrier 9 will, therefore, rotate 1.6363436 revolutions rearward in order for gears 23 and 24, together with carrier gear 33 to be driven forward one revolution.
  • the static gears 27 and 40 may be variable between the non- rotatable, fixed condition and a rotatable condition by the interposition of a clutch mechanism or the like between the gear and the stationary casing 3.
  • the device of Figure I is therefore, a simple version of a fully variable, constant-mesh transmission made possible by way of the off-set torque compensation applied to the main carrier 9.
  • the explanation indicates something of the possibilities of such a device, and the question as to what enables the transmission to know when to change gear is shown to be a function of the overlap torque working in favour of the rearward rotation of the main carrier 9.
  • This rearward rotational bias cannot simply allow the main carrier to rotate backwards producing negative output drive, as the ratios dictate that for every 1.6363636 revolutions of the main carrier in the rearward direction, the output gear 37 must rotate forwards one revolution.
  • the overlap torque on the main carrier 9 will diminish in direct relationship with the increase in rotational speed of the main carrier 9 and output gear 37. Indeed, at the I : I input/output ratio, there will be no overlap torque present. However, any slowing of the output will immediately cause overlap torque to be established and rearward emphasis to be applied to the main carrier. However, this will not be eroded if the output gear 37 is unable to accelerate, and if a disparity between input and output revolutions exists, then until the output can accelerate, the status quo will be maintained. A degree of torque increase will be present until the 1.6363636 rearward revolutions of the main carrier matches the I forward revolution of the input and output shafts.
  • the rearward overlap torque on the carrier 9 can be increased without a change in gear ratio being involved by retaining similar ratios but by increasing the length of the relevant lever arm, i.e. the distance between axes X-X and Z-Z. If this distance is increased to, say, 90mm, the off-set ratio will increase from 1.7446809 : I so that the 0.6060606T output from the planet gear 39 will again be multiplied by the 1.61 1 1 1 I I ratio between planet gear 39 and static gear 40 to give the resultant 0.9764309T, from which is subtracted the input value of 0.6060606T to give 0.3703703T as the rearward torque bias on the applied to the carrier 9 at axis Z-Z.
  • Figure 2 illustrates a second embodiment of the invention which is a variation of the layout depicted in Figure I .
  • the differential unit is placed within the output section of the transmission, and the input section includes an epicyclic/annular gear assembly capable of generating a k : I ratio.
  • a second transmission device embodying the invention comprises an input shaft 101 extending into a casing 102 through an input journal 103 of the casing and an output shaft 104 extending from the casing 102 through an output signal 105.
  • a free-running intermediate shaft 106 is located between the input and output shafts 101 and 104 by means of locating shaft portions 107 and 108 received in corresponding locating bores in the shafts 101 and 104.
  • a main carrier 109 is borne by the journals 103 and 105 and the intermediate shaft 106 so as to be independently rotatable about the same main axis X-X ⁇ s the shafts 101 , 104 and 106.
  • a differential unit of the device comprises a differential carrier 1 10 which is fixed to or part of the intermediate shaft 106 and presents stub axles I 1 1 and 1 12 which are fixed to or part of the carrier 1 10 first and second layshaft axles 1 13 and I 14 are fixed to or part of the main carrier 109 and support free-running sleeve layshafts I 15 and 1 16 for rotation about first and second subsidiary axes Y-Y and Z-Z.
  • An input gear 1 17 having 28 teeth is fixed to or part of input shaft 101 and engages epicyclic planet gears 1 18 and 1 19 having 42 teeth each and mounted on respective stub axles 120 and 121 which are fixed to or part of an epicyclic planet gear carrier 122 which is rotatable with intermediate shaft 106.
  • the planet gears 1 18 and 1 1 are engaged with an annular gear
  • Epicyclic output sun gear 124 has 47 teeth and is rotatable with annular gear 123 to which it is connected by sleeve shaft 125.
  • Sun gear 124 is engaged with a reference planet gear 126 having 47 teeth and rotatable with sleeve shaft 1 15 on the first axle 1 13.
  • Compound reference planet gear 127 has 36 teeth is rotatable with sahft 1 15 and engages a static gear 128 having 58 teeth and non-rotatably supported by casing 102 concentrically of main axis X-X.
  • a sun gear 129 having 123 teeth is mounted concentrically and rotatably on intermediate shaft 106 and is coupled for rotation with differential bevel gear 130 having 44 teeth and engaged with idler bevel gears 131 and 132 having 44 teeth and rotatably mounted on shaft axles I I I and ! 12.
  • the idler bevel gears 131 and 1 32 are also engaged with an output bevel gear 133 having 44 teeth and fixed to or part of output shaft 104.
  • Gear 129 is engaged with planet gear 134 having 123 teeth and rotatable with sleeve shaft I 16 on the second axle 1 14.
  • a compound planet gear 135 having 54 teeth is also rotatable with sahft 1 16 and engages a second static gear 136 having 87 teeth and non-rotatably carried by output journal 105 on a mounting flange 137.
  • Subsidiary axes Y-Y and Z-Z are radially spaced by 47.00mm and 82.00mm respectively from the main axis X-X.
  • the transmission device of Figure 2 can produce a bottom gear ratio of 2.5 : I and a top gear ratio of I : I .
  • the input epicyclic assembly produces (for each IT torque introduced) a torque of 4T upon the annular gear 123 in the opposite rotational direction to the torque applied to the input shaft 101 and a torque of 5T upon the epicyclic planet carrier 122 in the same direction as that on the input shaft 101.
  • the 5T torque is fed along the intermediate shaft 106 to the differential carrier 1 10 and the free-running idler bevel gears 131 and 132 by way of the stub-axles I I 1 and I 12, applying 2.50T to gear 133 and 2.50T to gear 130.
  • the 2. SOT applied to gear 133 is, of course, the 2.50T output drive, as gear 133 is rotatable with output shaft 104.
  • the 2.50T applied to gear 130 is the torque factor responsible for ultimately driving the main carrier 109 rearwards and it is applied to gear 129 from gear 130.
  • the 2.50T present upon gear 129 is applied to gear 134 causing it to rotate in a direction opposite to the input shaft 101.
  • gear 134 is compounded to gear 135, which is engaged with the static gear 136, the resultant engagements cause the main carrier 109 to be loaded in a direction opposite to the input shaft 101.
  • the 2.4444444T is applied to the main carrier 109 at the subsidiary axis Y-Y which is the centre of rotation of the sleeve shaft I 15.
  • the I .52777778T present at subsidiary axis Z-Z of axle 1 16 is multiplied by the off-set ratio of 1 ,7446809 between the two axes Z-Z and Y-Y, giving a total rearward torque of 2,6654847T, this being 0.22 I 0403T greater than the total forward loading applied to the main carrier 109 by way of axle I 15.
  • the required overlap torque and change-up drive is therefore established.
  • the rearward drive to the main carrier 109 is thus 0.06501 1 T greater than the forward drive (3.73 I 6785T - 3.6666666T).
  • This example indicates the flexibility of the invention.
  • Figure 3 illustrates a third transmission device which employs an output section similar to that of the Figure 1 embodiment and an input section similar to that of Figure 2.
  • an input shaft 201 extends into casing 202 through input journal 203 of the casing and an output shaft 204 extends from casing 202 through output journal 205.
  • a free-running intermediate shaft 206 is located between the input and output shafts 201 and 204 by means of locating shaft portions 207 and 208 received in corresponding locating bores in the shafts 201 and 204.
  • a main carrier 209 is borne by the journals 203 and 205 and the intermediate shaft 206 so as to be rotatable about the same axis X-X as the shafts 201 , 204 and 206.
  • First and second Iayshaft axles 213 and 214 are fixed to or part of the main carrier 209 and support free-running sleeve layshafts 215 and 216 for rotation about respective first and second subsidiary axes Y-Y and Z-Z.
  • Aninput gear 217 having 18 teeth is fixed to or part of input shaft 201 and engages epicyclic planet gears 218 and 219 having 27 teeth each and mounted on respective stub axles 220 and 221 which are fixed to or part of an epicyclic planet gear carrier 222 which is rotatable with intermediate shaft 206.
  • the planet gears 218 and 219 are engaged with annular gear 123 having 72 teeth and rotatably mounted on intermediate shaft 106 by annular gear carrier 223a.
  • Epicyclic output sun gear 224 has 47 teeth and is rotatable with annular gear 123 to which it is connected by sleeve shaft 225.
  • Sun gear 224 is engaged with reference planet gear 226 having 47 teeth and rotatable with sleeve shaft 215 on the first axle 213.
  • Compound reference planet gear 227 has 36 teeth, is rotatable with shaft 215 and engages static gear 228 having 58 teeth and non-rotatably supported by casing 202 concentrically of main axis X-
  • a sun gear 229 having 32 teeth is fixed to or part of input shaft 201 and engages planet gears 230 and 231 having 24 teeth each and rotatable with respective planet layshafts 232 and 233 rotatably carried by a carrier gear 234 having an external gear face 235 provided with 123 teeth.
  • Compound planet gears 236 and 237 having 30 teeth each are also rotatable with layshafts 232 and 233 respectively and engage an output sun gear 238 which is fixed to or part of output shaft 204 and has 26 teeth.
  • carrier gear 234 is engaged with a planet gear 239 having 123 teeth and rotatable with sleeve shaft 21 6 which also carries a compound planet gear 240 having 54 teeth and engaged with a second static gear 24 1 having
  • Subsidiary axes Y-Y and Z-Z are radially spaced by 32.25mm and 82.00mm respectively from main axis X-X, giving an off-set ratio of 2.326241 1 : I .
  • gear 229 wil l be provided with 5T also in the forward direction, with gear 224 being provided with 4T in the reverse direction.
  • 4T (58 36) 6.4444444T to static gear 228.
  • the 5T forword loading of gear 229 is applied to the engaged planets 230 and 231 at a ratio of 24 » 32 providing layshaft 232 and 233 with 3.75T.
  • the 2.4444444T forward loading of the main carrier 209 is now met with only 1.0694444T of rearward loading.
  • the off set ratio of 2.326241 I I between axes Y-Y and Z-Z has been included.
  • the layshaft combination 21 3, 215 is only 35.25mm radially out 0 from the centre rotation of the main carrier 209, while the combination 2 14, 216 is 82.00mm radially out from the rotating centre of the main carrier 209. Therefore, multiplying the I .0694444T by the off -set ratio 2.326241 I gives 2.4877855T effective rearward drive to the main carrier 209.
  • the torque applied to the main carrier 0 at axis Z-Z is always multiplied by the off-set ratio in order to discover the overlap.
  • this is for convenience only and even if the torque present at axis Y-Y is divided by the off-set ratio, the overlap always comes out in favour of the effective torque being in favour of axis Z-Z. 5
  • Figure 4 is an all-spur, fully variable constant mesh transmission device which includes a single rotating carrier mechanism. -13-
  • input shaft 301 extends into casing 302 through input journal 303 and output shaft 304 extends from the casing 302 through output journal 305, the shafts being coaxially located by locating shaft portion 306 of output shaft 304 rotatably engaging in a corresponding locating bore of
  • a main carrier 309 is borne by the casing 302 and shaft 304 for rotation about the same main axis X-X as the shafts 301 and 304.
  • a pair of first layshafts 310, 31 1 are rotatably mounted on main carrier 309 for
  • a pair of third layshafts 314, 31 5 are rotatably supported by the
  • the output shaft 304 carries first and second adjacent, independently rotatable inner sleeve shafts 316 and 317 and an outer sleeve shaft 318 rotatably mounted on the first inner sleeve shaft 31 .
  • An input gear 320 having 75 teeth is fixed to or part of input shaft 301 and engages planet gears 321 , 322 having 75 teeth each respectively rotatable with layshafts 310, 31 1 which also carry respective compound planet gears 323, 324 having 60 teeth.
  • Gears 323, 324 engage sun gear 325 5 which is fixed to or part of sleeve shaft 318 and has 90 teeth.
  • Compound sun gear 326 is connected to sun gear 325 by sleeve shaft 318, has 60 teeth and is engaged with planet gears 327, 328 having 60 teeth and rotatable with layshafts 314, 31 5 respectively whcih also carry respective compound planets gears 329, 330 having 30 teeth.
  • Sun gear 331 is fixed to or part of 0 sleeve shaft 317 and is engaged with compound planet gears 329, 330.
  • Sleeve shaft 317 connects gear 331 to sun gear 332 which has 36 teeth and is engaged with planet gears 333, 334 carried by layshafts 312, 313 respectively and having 24 teeth.
  • Layshafts 312, 313 connect gears 333, 334 to respective compound planet gears 335, 336 which have 30 teeth and are engaged with output gear 337 which is fixed to or part of the output shaft
  • the axes Z-Z are spaced at 75.00mm from axis X-X and the axes Y-Y at 25.00mm.
  • gears 320, 321 , 323 will load gear 325, in the same rotational direction as the input shaft with
  • the I .5T is transmitted along sleeve shaft 318 to gear 326, this being engaged at a ratio of I : I with gear 327, so that the I .5T is then transmitted along the layshoft 314 directly to gear 329.
  • Gear 329 is engaged at a ratio of 3 : I with gear 331. Therefore, gear 331 is forward loaded in the same direction as the input shaft with 4.5T. This 4.5T is now transmitted along sleeve shaft 1 17 to gear 332, thereby loading this gear the forward direction with the 4.5T.
  • the 4.5T has been divided into two parts: 3T applied directly to the output and I .5T to the main carrier 309 in the same direction as input shaft 301.
  • layshaft 310 is applying 0.5T rearwards torque drive to carrier 309 and, at the same time, layshaft 313 is applying 1.5T in a forward direction to main carrier 309.
  • I off-set advantage gives I .5T effective loading. This is a perfect balance with the I .5T (forward) as applied to the main carrier 309 by layshaft 313. If an overlap torque in a rearward direction is required, as in previous examples, then for example by extending the 75.00mm to 80.00mm, there would be on overlap in favour of rearward main carrier 309 rotation, of 0.IT.
  • Figure 4 is, therefore, an embodiment of the invention which uses a single carrier device, shared by the two contradictory torques.
  • Figure 5 illustrates a fifth embodiment using the same off-set techniques, but in conjunction with fixed (case-held) annular gears.
  • the overlap in this instance is in favour of forward rotation of the main carrier, rather than rearward rotation as previously described.
  • input shaft 401 extends into casing 402 through input journal 403 and output shaft 404 extends from the casing through output journal 405.
  • First and second intermediate shafts 406 and 407 are independently rotatably located between input and output shafts 401 and 404 by means of locating studs 408, 409 and 410 received in corresponding locating bores in the input shaft, second intermediate shaft and output shaft.
  • Two first layshafts 41 I and 41 2 are rotatably carried by casing 402 for rotation about respective subsidiary axes Z-Z equally spaced from the main axis X-X of rotation of the input and output shafts.
  • a pair of second layshafts 413 and 414 are carried by a carrier gear 415 rotatable on second intermediate shaft 407, the layshafts 413, 414 defining respective second subsidiary axes Y-Y.
  • a main carrier 416 rotatable on shaft 407 presents two stub axles 41 7, 418 which are fixed to or part of the carrier 416.
  • An annular carrier 41 is rotatable with the first intermediate shaft 406.
  • An input gear 420 having 25 teeth is fixed to or part of input shaft
  • Carrier gear 425 receives the stub axles 423, 424 and engages planet gear 426 rotatable with layshaft 41 I and having 40 teeth.
  • Sun gear 429 is also rotatable with layshaft 41 1 and has 40 teeth, gear 427 engaging sun gear 428 having 100 teeth and fixed to second intermediate shaft 407.
  • Sun gear 429 has 30 teeth and is also fixed to or part of intermediate shaft 407.
  • Sun gear 429 is engaged with planet gears 430, 431 having 26 teeth and rotatable with layshafts 413, 414.
  • Compound planet gears 432, 433 are rotatable with layshafts 13, 14, have 30 teeth and engage output gear 434 having 26 teeth and fixed to or part of output shaft 404.
  • Planet gears 421 , 422 engage annular gear 435 having 105 teeth which >s fixed to or part of carrier 419 which is itself fixed to the first intermediate shaft 406.
  • Sun gear 436 has 24 teeth and is fixed to or part of intermediate shaft 406 and engages planet gears 437, 438 having 20 teeth and engaged with a fixed annular gear 439 having 64 teeth.
  • Planet gears 437, 438 are carried by stub axles 440, 441 which are fixed to or part of a sun gear 442 having 100 teeth.
  • Gear 442 is rotatable on the first intermediate shaft 406 and engages planet gear 443 having 40 teeth and rotatable with layshaft 412.
  • Compound planet gear 444 also has 40 teeth and is rotatable with layshaft 412.
  • Gear 444 is engaged with sun gear 445 which has 100 teeth and is rotatable with main carrier 416.
  • Planet gears 446, 447 rotatable about stub axles 417, 418 have 70 teeth and engage a second fixed annular gear 448 having 224 teeth.
  • the axes Z-Z are spaced at 77.00mm from axis X-X and the axes Y-Y at 22.00mm.
  • the 5.2T will be passed on to the layshaft 41 I via the engagement between gears 425 and 426, this being at a ratio of 0.4: 1 , and subsequently from layshaft 41 1 via gear 427 to gear 428 at a ratio of 0.25 : I . Therefore, geor 428 will be driven forward ⁇ t 5.2T.
  • annular gear 435 will cause 4.2T to be applied to sun gear
  • the I 5.4T will be passed via a 0.4 : 1 /0.25 : I series of engagements ' ⁇ to eventually drive gear 445 rearwards with 15.4T.
  • the main carrier 4 16 is already subjected to a rearward loading of I 5.4T and, therefore, the 4.7458425T forward drive must be now adjusted by way of multiplication of the off-set 0 ratio 4.7458425T x 3.5 : I . Therefore, the avai lable 4.7458425T becomes an effective 16.6 10449T as far as the I 5.4T of rearward loading is concerned, creating an overlap torque of 1.2 I 04488T in favour of forward rotation of the main carrier 41 .
  • This transmission can, therefore, provide fully variable, constant- mesh (load sensitive) forward drive with a range of I : I to 3.9057775 : I and reverse gear. Furthermore, by allowing one or both annular gears to be braked to case in a gradual fashion, a clutching action can be included.
  • Figure 6 represents a departure from the basic principles, in that, the off-set loading of a carrier component is replaced by an off-set resulting from a disparity in related compound diameters; i.e. two gears of differing size and tooth-count.
  • input shaft 501 extends into casing 502 through input journal 503 and output shaft 504 extends from casing 502 through output journal 505.
  • An intermediate shaft 506 is located between the input and output shafts by locating shaft portions 507, 508 borne in corresponding locating bores of the input and output shafts.
  • An annular gear carrier 509 is fixed to or part of a first sleeve shaft 510 which is rotatably received on intermediate shaft 506 and lies adjacent a second sleeve shaft 507 also rotatable on shaft 506.
  • Input gear 520 has 26 teeth and is rotatable with input shaft 501 and engages idler gears 521 , 522 having 39 teeth and mounted on stub axles 523, 524 which are fixed to or part of a planet gear carrier 525.
  • Gears 521 , 522 are engaged with annular gear 526 having 104 teeth and fixed to or part of carrier 509.
  • Sleeve shaft 510 carries a sun gear 527 having 32 teeth and engaged with planet gear 528 having 20 teeth.
  • Gear 528 is rotatable with l ⁇ ysh ⁇ f t 529 which is borne by the casing 502 and carries a compound planet gear 530 having 16 teeth.
  • Sleeve shaft 507 carries a sun gear 531 having 36 teeth and engaged with planet gear 530.
  • Sun gear 532 has 144 teeth, is rotatable with sleeve shaft 507 and engages planet gear 533 carried by layshaft 534 borne by the casing 502.
  • Compound planet gear 535 is also rotatable with the layshaft 534 and has 80 teeth.
  • Gear 535 is engaged with carrier gear 536 having 40 teeth and carrying layshafts 537 and 538.
  • Gear 536 is rotatable on the intermediate shaft 506.
  • Sun gear 539 is fixed to or part of intermediate shaft 506 and has 36 teeth.
  • Gear 539 is engaged with planet gears 540, 541 which are rotatable with layshafts 537, 538 respectively and have 36 teeth.
  • Compound planet gears 542, 543 are rotatable with layshafts 537, 538 have 40 teeth and engage output gear 544 which is fixed to or part of output shaft 504.
  • the 5T output from the input epicyclic unit delivers its torque (via the intermediate shaft 506) to sun gear 539, causing this gear to be forward loaded with 5T.
  • This perfectly balanced situation can, of course be altered by adjusting the indicated radial contact points. For example, by extending the
  • the off -set ratio will be incre ⁇ sed to ⁇ new figure of 4.3333333 : I , thereby increasing the capability of the I .40625T to 6.09375T at the point of engagement between gears 530 and 531.
  • the result is a rearward overlap torque in favour of a forward rotation of the compound assembly 531 , 507, 532.
  • Gears are, in all respects, simply repetitive levers, and as such they must conform to the characteristics of levers. Therefore the various items shown in this specification are viewed in light of two basic factors, i.e. the diametric pitch of the point of contact (the establishment of the leverage one upon another) and the number of teeth contained peripherally, in relation to another so engaged (the establishment of the interrelated speeds). These two, quite separate factors are quite often, and quite wrongly, interpreted as being each the direct result of the other. However, as rotational speeds are often directly quantifiable in relation with resultant torques, the confusion is understandable. It is more clearly demonstrated however by mechanisms utilising more than one gear component, i.e. a standard differential, than by two engaged gear items.
  • Figure 6 uses a compound gear section as a means of providing an off-set leverage situation without incurring contradictory tooth ratio problems.
  • gear rotational speed ratios remain constant. (Thus, if assembly 531 , 507, 532 were itself rotated one revolution in either direction) then we would find that gear 532 would cause gear 533 to rotate 1 1 6 - 2.25 times, and this multiplied by the number of teeth present upon gear 535 (80) would be the number of teeth fed to gear 536, and gear
  • this subsequent I : I gear would also require being 104.00mm in diameter.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Arrangement Of Transmissions (AREA)

Abstract

Un dispositif de transmission comprend un arbre d'entrée (1) et un arbre de sortie (2) tournant autour d'un axe principal (X-X). Un arbre intermédiaire (6) est placé entre l'arbre d'entrée et l'arbre de sortie et une plaque-support principale (9) tourne autour de l'axe principal dans un logement fixe (2) du dispositif. Un assemblage à engrenages différentiels (10-12, 20-23) fournit une première sortie de référence pour des engrenages planétaires (25, 26) montés sur la plaque-support (9) en vue de leur rotation autour d'un premier axe secondaire (Y-Y), l'engrenage planétaire (26) s'engageant avec un engrenage fixe (27). L'assemblage à engrenages différentiels fournit une seconde sortie, par l'intermédiaire d'un engrenage principal (28) tournant avec un support différentiel (10), à des engrenages planétaires de sortie (29, 31), qui entraînent l'arbre de sortie et sont soutenus par un engrenage de support (33), lequel entraîne d'autres engrenages planétaires (38, 39) soutenus par la plaque-support (9) en vue de leur rotation autour d'un deuxième axe secondaire (Z-Z), l'engrenage (39) s'engageant avec un second engrenage fixe (40).
PCT/GB1987/000129 1986-02-22 1987-02-20 Transmissions a auto-reglage Ceased WO1987005085A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB868604461A GB8604461D0 (en) 1986-02-22 1986-02-22 Self-adjusting transmissions
GB8604461 1986-02-22

Publications (1)

Publication Number Publication Date
WO1987005085A1 true WO1987005085A1 (fr) 1987-08-27

Family

ID=10593536

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1987/000129 Ceased WO1987005085A1 (fr) 1986-02-22 1987-02-20 Transmissions a auto-reglage

Country Status (4)

Country Link
EP (1) EP0258368A1 (fr)
AU (1) AU7082587A (fr)
GB (2) GB8604461D0 (fr)
WO (1) WO1987005085A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2321505B (en) * 1997-01-27 2001-04-25 Arnold Derek Child Mechanical torque converter

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR861196A (fr) * 1939-07-21 1941-02-03 Transmission à vitessse variable
FR1074132A (fr) * 1953-02-07 1954-10-01 Convertisseur de couple
FR1165580A (fr) * 1956-12-01 1958-10-27 Convertisseur de couple
FR1323617A (fr) * 1962-02-27 1963-04-12 Variateur de vitesse mécanique à couple variable
FR1472243A (fr) * 1966-01-28 1967-03-10 Convertisseur mécanique de couple
GB1287236A (en) * 1969-11-21 1972-08-31 Edward Hartley Clay Improvements in and relating to gear boxes
EP0014578A1 (fr) * 1979-02-06 1980-08-20 Rafael Perlin Mécanisme de transmission automatique et continue
GB2160598A (en) * 1984-05-19 1985-12-24 Mechadyne Transmissions Limite Self regulating transmission

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB548941A (en) * 1941-01-22 1942-10-30 Leslie Adcock Koevort Improved power-transmission means for motor vehicles
GB679565A (en) * 1949-11-30 1952-09-17 Peter Herbert Cleff Improvements in or relating to two-speed gearing

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR861196A (fr) * 1939-07-21 1941-02-03 Transmission à vitessse variable
FR1074132A (fr) * 1953-02-07 1954-10-01 Convertisseur de couple
FR1165580A (fr) * 1956-12-01 1958-10-27 Convertisseur de couple
FR1323617A (fr) * 1962-02-27 1963-04-12 Variateur de vitesse mécanique à couple variable
FR1472243A (fr) * 1966-01-28 1967-03-10 Convertisseur mécanique de couple
GB1287236A (en) * 1969-11-21 1972-08-31 Edward Hartley Clay Improvements in and relating to gear boxes
EP0014578A1 (fr) * 1979-02-06 1980-08-20 Rafael Perlin Mécanisme de transmission automatique et continue
GB2160598A (en) * 1984-05-19 1985-12-24 Mechadyne Transmissions Limite Self regulating transmission

Also Published As

Publication number Publication date
GB8604461D0 (en) 1986-03-26
AU7082587A (en) 1987-09-09
GB8703979D0 (en) 1987-03-25
GB2187243A (en) 1987-09-03
EP0258368A1 (fr) 1988-03-09

Similar Documents

Publication Publication Date Title
US6059685A (en) Coaxial traction drive automatic transmission for automotive vehicles
US4976670A (en) Power transmission
CA2002070C (fr) Systeme de transmission a rapports multiples
US4109551A (en) Variable speed gear ratio transmission apparatus
US6007450A (en) Five speed planetary transmission
US4762022A (en) Torque retaining and proportioning differential drive assembly
US4235125A (en) Automatic stepless transmission
US2761333A (en) Epicyclic change-speed gear
EP0771970A3 (fr) Transmission continue toroidale
EP0775851B1 (fr) Transmission de puissance à rapports multiples
JPH05196103A (ja) 変速装置
US4954123A (en) Radial helix drive horse power amplifier
US3733928A (en) Speed change gear device
US5554079A (en) Gear train of an automatic five-speed transmission for a vehicle
US5707312A (en) Multi-speed power transmission
WO1987005085A1 (fr) Transmissions a auto-reglage
US5904633A (en) Continously variable transmission
SE457198B (sv) Automatisk stegloes kraftoeverfoering
EP0242338B1 (fr) Système de transmission pour véhicule automobile
GB2219640A (en) Drive transmission apparatus
EP0258369A1 (fr) Transmissions a auto-reglage
US3835731A (en) Power transmission apparatus
US2229338A (en) Gearing device
GB1600001A (en) Power transmission systems
US5358459A (en) Mechanic drive apparatus

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AU BB BG BR DK FI HU JP KP KR LK MC MG MW NO RO SD SU US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CF CG CH CM DE FR GA GB IT LU ML MR NL SE SN TD TG