WO2002073068A1 - Transmission a rapport variable - Google Patents

Transmission a rapport variable Download PDF

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Publication number
WO2002073068A1
WO2002073068A1 PCT/ZA2002/000026 ZA0200026W WO02073068A1 WO 2002073068 A1 WO2002073068 A1 WO 2002073068A1 ZA 0200026 W ZA0200026 W ZA 0200026W WO 02073068 A1 WO02073068 A1 WO 02073068A1
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WO
WIPO (PCT)
Prior art keywords
skew
drum
ring
shaft
variable ratio
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/ZA2002/000026
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English (en)
Inventor
Philip Ulrich Wieland
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
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of WO2002073068A1 publication Critical patent/WO2002073068A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
    • F16H29/04—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts

Definitions

  • This invention lies in the field of drive transmissions, that is, machines for transmission of a mechanical drive from an input to an output.
  • the invention is concerned with the provision of a variable ratio drive transmission especially a design, which can achieve a wide range of stepless ratio variation.
  • Light industrial and agricultural vehicles can use the transmission.
  • Winches can advantageously use the transmission due to the wide range of torques and speeds available.
  • High ratio reduction gearboxes can be provided.
  • the present invention works with a device that is analogous to a swash plate, but perhaps better called a skew drum, for present purposes and this term must be understood as including swash plates.
  • a variable ratio drive transmission includes an input shaft, a skew drum mounted at an end of the shaft, the plane in which the periphery of the drum lies being inclined at an angle with the axis of rotation of the shaft, means for adjusting that angle, at least one connector which is non-rotationally linked to the periphery so as to reciprocate without rotation, during rotation of the skew drum, whereby change of the angle of the skew drum varies the stroke of reciprocation accordingly, the connector connecting the reciprocating motion to a means which transmits only one direction of reciprocation to provide unidirectional rotation of an output shaft at variable speeds according to variation of the skew drum angle.
  • the attachment of the skew drum to the end of the shaft may be by means of a hinge structure with a control means whereby the angle of the drum to the axis of rotation of the shaft may be varied between ninety degrees (or orthogonal to the shaft axis) and an inclined (non-orthogonal) angle.
  • the control means may be a link having a first end axially movable along the shaft and the second connected to the drum; the first end of the link may be moved by a non-rotational control means by a rotationally free connection.
  • the connector may take several forms and be operationally linked in several ways.
  • One form of connector is a rod, which is pivotally connected to a crank on the output shaft.
  • the opposite end of the rod may be operationally linked by being connected to a ring, which is held against rotation and slides against the skew drum periphery.
  • the skew drum has a thrust bearing which allows the input shaft to rotate freely within, which allows the outer rim of the skew drum to stand still (not rotate) but oscillate; the rods are connected to this. In either arrangement the oscillation is transferred via the connecting rods to the lever arms of the output shaft.
  • the skew ring can be prevented from rotating by a pin fixed to it, which slides in a groove of a part which is fixed to the outer housing of the gearbox.
  • the opposite end of the rod to the output shaft may be connected to a gimbal or other type of universal joint in which a rotationally slipping connection can be arranged to transmit only oscillation and not rotation.
  • More than one connector arranged to reciprocate out of phase with each other is advantageous because the impulses transmitted to the output shaft per rotation thereof can be increased, giving smoother output.
  • a skew drum has a skew ring with a bearing interposed between the drum periphery and the skew ring, the skew ring pivotally connected by pivots at diametrically opposite positions to a gimbal ring, which in turn is pivotally connected by pivots to a non-rotational frame, the pivots being located on mutually orthogonal and intersecting axes.
  • the connector(s) preferably in the form of rods, is/are pivotally connected to the gimbal ring.
  • the gimbal ring may be omitted and another means of preventing rotation of the skew ring provided.
  • the means to transmit only one direction of reciprocation may comprise one-way clutch in a bush around the output shaft with a crank fixed to the clutch.
  • the connector giving an angular oscillation of the crank and hence bush will transmit rotational impulses only in one direction.
  • the clutch may be of a known kind, having a balls or rollers in a multiple tapered hub and shaft, giving a ratchet-like function.
  • a flywheel can if desired be provided on the output shaft to give smother output rotational speed and torque.
  • an extra swash plate (skew drum) can be added to the input shaft on the opposite side of the output shaft to balance the reciprocating forces.
  • This skew drum will also have its own set of connecting rods and levers with one-way bearings connected to the output shaft. This would also double the output torque of the gearbox.
  • the smoothness of power transfer from the skew drum can be improved substantially by the addition of lever arms to the output shaft and connecting rods between the levers and the outer ring of the skew drum.
  • a second shaft running parallel to the output shaft and connected by two gears in mesh so that the shafts turn in opposite directions, can be added. It must be remembered that the levers must be divided equally between the two shafts. This will increase the gearboxes smoothness, output torque as well as the output speed of the box due to the fact that there are more pulses per revolution of the output shaft.
  • electrical clutches can be installed instead of using one way bearing clutches.
  • the clutches would have to be controlled by CPU and engaged and disengaged at the right time to create either forward or reverse motion.
  • FIG. 13 show a first embodiment
  • figure 14 shows another embodiment
  • figure 1 is an elevation showing the external casing, input and output shafts and ratio control rod,
  • figure 2 is an isometric view of the inner workings of the transmission
  • figure 2A is a similar view to figure 2, with the output shaft sectioned,
  • figure 3 is a cross sectional view of the transmission, with the sectioning plane passing through the input shaft,
  • FIGS. 4 to 8 are various views of components of the transmission
  • figure 14 shows another embodiment.
  • the drive transmission 1 has the mechanism housed in a rectangular casing 2 with input shaft 3 and output shaft 4 and control handle 5. With a constant input shaft speed being maintained, the output shaft speed can be varied continuously from zero to a high speed by moving the control handle. Moved to the right 6 for higher speed and to the left 7 for lower speed.
  • the transmission ratio and hence output speed can be varied by very small increments indeed and is essentially "infinitely" variable i.e. by infinitesimally small increments.
  • FIGS 2 and 2A and 3 show the general arrangement of the mechanism, which is located inside the casing.
  • the input shaft 3 has a skew drum 8 mounted on the interior end 9 of the shaft at an inclined angle 10 to the axis of rotation 11.
  • the angle can be varied from orthogonal (at right angles or ninety degrees) to the shaft axis 11 to a maximum inclination shown in figure 3 of 53 degrees.
  • the control of the angle of the skew drum is by means of the handle 5.
  • This has a slotted hole 12 pivoted on a pin 13 in the casing and ending in a yoke 14, which embraces and is pivotally connected by pins 15 to a collar 16.
  • the collar is connected by a bearing 17 to a bush 18, which allows the bush freely to rotate inside the collar but for an axial displacement of the bush to be effected by the handle.
  • the bush is pivotally connected by means of lugs 19 and pin 20 to a link 21 whose opposite end is pivotally connected by pin 22 to lugs 23 which are fixed to the skew drum 8.
  • the skew drum (see also figure 6) has a slotted hole 24 in its centre and an orthogonal diametral hole 25.
  • a disc 26 (see also figures 7 and 8) fits into the slotted hole and is held there by a pin (not shown) which passes through the diametral hole in the drum and a hole 27 in the disc.
  • a hole 28 in the disc fits over the end of the shaft and is fixed in this position.
  • a bearing 29 is fitted around the periphery of the skew drum and a skew ring 30 (see also figure 4) fits around the bearing. This allows the skew drum to rotate while the skew ring remains non-rotational, but oscillating according to the inclination of the skew drum on the input shaft.
  • the skew ring has diametral holes 31 and 32 which allow the skew ring to be connected by pins 33 to diametral holes 34 and 35 in a gimbal ring 36 (figure 5).
  • Orthogonal diametral holes 37 and 38 in the gimbal ring allow pins 39 and 40 to be carried in bearings 41 and 42 which are mounted bushes 43 and 44 fixed in the casing of the transmission.
  • Two rods 45 and 46 are pivotally connected by means of pivots on lugs47 and 48 which are fixed on the gimbal ring.
  • the opposite ends of the rods are pivotally connected by means of pivots on cranks 49 and 50 which are fixed to bushes 51 and 52 respectively.
  • roller clutches 53 and 54 Between these bushes and the output shaft are roller clutches 53 and 54 which transmit movement only in one direction. The resulting effect is that reciprocation of the rods provides rotational impulses to the output shaft in one direction only.
  • a reversing gearing (not shown) can be provided for to allow selection of a reverse direction of drive, if required.
  • the output shaft is held in bearings 55 and 56 in mounting blocks 57 and 58 respectively, with suitable spacers on the shaft.
  • the skew drum As the handle is moved to the right to a position shown in figure 10, the skew drum is moved into an inclined angle theta to the orthogonal. Rotation of the input shaft then causes an oscillatory movement of the gimbal ring, reciprocation of the rods and hence rotation of the output shaft. If the angle theta is small the output rotational speed is small, but the mechanical advantage is proportionally high. This provides a very high starting torque as the handle is moved towards a position which starts rotation, a significant advantage.
  • the rotational position of the skew plate shown in figure 10 is such that the two rods are at an intermediate position of their reciprocation, moving in opposite directions.
  • figure 11 shows the input shaft and hence skew ring having rotated through ninety degrees.
  • the gimbal has oscillated anti-clockwise if viewed from the top and the one crank is moving one way and the other the other way.
  • the one crank is imparting a rotational impulse via its clutch to the output shaft while the other is executing a return stroke with its clutch free-wheeling.
  • control handle is merely exemplary and control could be by other means, including automated, feedback remote controlled actuators or logic controlled means etcetera.
  • the casing unit could house further gearing of various conventional kinds, for example, a differential or a brake, etcetara.
  • Figure 14 shows an embodiment, which is the same as the preceding one except that instead of using the gimbal arrangement to prevent rotation of the skew ring, a pin 60 is fixed to the skew ring and oscillates in an arcuate shaped slot 61 fixed in the housing.
  • the mechanism is immersed in oil in its housing, so lubricating the action of the pin in the slot.
  • the load on the pin is slight being the "frictional" resistance of the bearing 29.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne une transmission d'entraînement pouvant être utilisée afin de donner régulièrement des rapports variables divers, dans un appareil fixe notamment à mises sous tension sans appel de courant et à différences de forte charge et dans des véhicules nécessitant un large éventail de rapports et de couples. La transmission comprend un tambour oblique (8) (ou un type de plateau incliné fixe) monté sur un arbre primaire (3) avec un angle variable d'inclinaison par rapport à l'arbre, un anneau oblique monté à l'aide d'un palier intercalé (30) sur le tambour, un anneau de cardan (36) pivoté au niveau de pivots diamétralement opposés (33) à l'anneau oblique et au niveau de pivots diamétralement opposés (34) orthogonaux au cadre de support par rapport au premier pivot mentionné. Des bielles de liaison (45, 46) sont reliées pivotantes à l'anneau de cardan et aux bras de manivelle (49, 56) qui sont à leur tour montés à l'aide d'embrayages à roue libre (51, 52) sur un arbre secondaire (4). La variation de l'angle du tambour oblique fait varier la vitesse de l'arbre secondaire, régulièrement variable de zéro à un maximum. L'angle formé entre le tambour oblique et l'arbre primaire est varié par un organe de commande, afin de donner cet entraînement variable.
PCT/ZA2002/000026 2001-03-13 2002-03-11 Transmission a rapport variable Ceased WO2002073068A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0106112A GB0106112D0 (en) 2001-03-13 2001-03-13 Variable ratio transmission
GB0106112.6 2001-03-13

Publications (1)

Publication Number Publication Date
WO2002073068A1 true WO2002073068A1 (fr) 2002-09-19

Family

ID=9910530

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/ZA2002/000026 Ceased WO2002073068A1 (fr) 2001-03-13 2002-03-11 Transmission a rapport variable

Country Status (2)

Country Link
GB (1) GB0106112D0 (fr)
WO (1) WO2002073068A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104879470A (zh) * 2015-06-12 2015-09-02 朱文雄 一种往复式无级变速器

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR538532A (fr) * 1921-07-20 1922-06-10 Changement de vitesse
US1733024A (en) * 1928-11-03 1929-10-22 Laub Adolf Variable-speed apparatus
US1863639A (en) * 1928-04-16 1932-06-21 Runkle Ella Transmission device for automotive vehicles
DE2206101A1 (de) * 1972-02-09 1973-08-30 Franz Riedl Stufenlos regelbares getriebe mit einem taumelscheibenartig gelagerten glied
CH684357A5 (de) * 1991-03-28 1994-08-31 Eduard Kaufmann Stufenlos verstellbares Getriebe.
WO1999040344A1 (fr) * 1998-02-06 1999-08-12 Lucas, Brian, Ronald Transmission a changement de vitesses continu

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR538532A (fr) * 1921-07-20 1922-06-10 Changement de vitesse
US1863639A (en) * 1928-04-16 1932-06-21 Runkle Ella Transmission device for automotive vehicles
US1733024A (en) * 1928-11-03 1929-10-22 Laub Adolf Variable-speed apparatus
DE2206101A1 (de) * 1972-02-09 1973-08-30 Franz Riedl Stufenlos regelbares getriebe mit einem taumelscheibenartig gelagerten glied
CH684357A5 (de) * 1991-03-28 1994-08-31 Eduard Kaufmann Stufenlos verstellbares Getriebe.
WO1999040344A1 (fr) * 1998-02-06 1999-08-12 Lucas, Brian, Ronald Transmission a changement de vitesses continu

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104879470A (zh) * 2015-06-12 2015-09-02 朱文雄 一种往复式无级变速器

Also Published As

Publication number Publication date
GB0106112D0 (en) 2001-05-02

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