WO2007030840A1 - Extension de la plage des rapports d'une transmission - Google Patents

Extension de la plage des rapports d'une transmission Download PDF

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Publication number
WO2007030840A1
WO2007030840A1 PCT/ZA2006/000100 ZA2006000100W WO2007030840A1 WO 2007030840 A1 WO2007030840 A1 WO 2007030840A1 ZA 2006000100 W ZA2006000100 W ZA 2006000100W WO 2007030840 A1 WO2007030840 A1 WO 2007030840A1
Authority
WO
WIPO (PCT)
Prior art keywords
ratio range
primary transmission
ratio
transmission
range extension
Prior art date
Application number
PCT/ZA2006/000100
Other languages
English (en)
Inventor
Johannes Jacobus Naude
Original Assignee
Johannes Jacobus Naude
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 Johannes Jacobus Naude filed Critical Johannes Jacobus Naude
Publication of WO2007030840A1 publication Critical patent/WO2007030840A1/fr

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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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
    • F16H2037/025—CVT's in which the ratio coverage is used more than once to produce the overall transmission ratio coverage, e.g. by shift to end of range, then change ratio in sub-transmission and shift CVT through range once again

Definitions

  • This invention relates to a method of and an arrangement for increasing the ratio range of a primary transmission system.
  • a problem arises if the primary transmission is a continuously variable transmission (CVT) or sequential type transmission since neither can be shifted sequentially quickly through all of its gears.
  • CVT continuously variable transmission
  • sequential type transmission since neither can be shifted sequentially quickly through all of its gears.
  • a transmission system which, to an extent, solves this problem is described in the specification of American patent No. US 4,682,511.
  • This transmission utilises planetary gearing power loops to act as power splits by the employment of a combination of clutches and gearbox variable gear sets.
  • a major disadvantage to a transmission of this type is, however, that the percentage of power available that passes through the primary transmissions (in the above case a variable belt and pulley CVT) varies as the ratio of the CVT varies. In this situation where the ratio range of the primary transmission is decreased the planetary loops result in a true power split which causes only a percentage of the total power being transmitted to pass through the primary transmission.
  • This type of power split is typically used in conjunction with friction drive CVT's such as belt and pulley systems, toroidal systems and hydrostatic CVTs as the primary transmission as these CVT's usually have a large ratio range but have low mechanical efficiencies.
  • the percentage portion of the available power passing through the primary transmission reduces the percentage loss in the overall power transmission system but decreases the transmission range which in turn requires multiple ranges or modes of operation as is the case with the subject matter of patent No. US 4,682,511 which employs four modes of operation.
  • the four modes of operation results in four distinct power/planetary loops acting as four power splits, to compensate for the ratio range reduction of the primary transmission (CVT), wherein the power from each mode flows simultaneously in a dual forward direction through the CVT as well as through the selected gearbox and engaged clutch to be combined in the common planetary gearing.
  • Friction drive CVT's additional have to cope with the inherent torque limitations created by the friction drive interface which also makes power splits an attractive solution.
  • linear power path in this specification is to be taken to mean a power path which is not deviated by planetary gearing or the like into power loops or splits.
  • a method of extending the ratio range of a primary transmission according to the invention includes the steps of:
  • the primary transmission the ratio range extension arrangement may each have distinct power input and output shafts with the method including the steps of :
  • the switching means may be clutches with: a clutch of a first pair of clutches is located in the first power path between the ratio range extension arrangement input shaft and the input shaft to the primary transmission and the second between the primary transmission output shaft and the ratio range extension arrangement output shaft,
  • a clutch of a second pair of clutches is located in the second linear power path between the ratio range extension arrangement input shaft and the primary transmission output shaft and the second between the primary transmission input shaft and the ratio range extension arrangement output shaft,
  • the method includes the steps of activating the first pair of clutches, while the second pair are disengaged, to supply power in the first linear power path from the ratio range extension arrangement input shaft to its output shaft, and
  • a transmission ratio range extension arrangement may include:
  • the ratio range extension arrangement may include:
  • a power input shaft which is drivingly engaged with the first drive train arrangement and is, in use, driven by a prime mover
  • coupling means in each drive train arrangement for selectively coupling one or the other of the primary transmission input or output shafts to the first drive train and the remaining shaft to the second drive train,
  • switch means which, in a first mode of operation, in use, activates the coupling means to couple the primary transmission input shaft to the first drive train and its output shaft to the second drive train to cause power to flow, in a first linear power path, from the ratio range extension arrangement input shaft, through the primary transmission in its normal mode of operation, and to the ratio range extension arrangement output shaft, and
  • the coupling means in both drive train arrangements, may comprise:
  • the ratio range extension arrangement input shaft may include fixed rotatable means for driving the first drive train and its output shaft includes fixed rotatable means which is driven by the second drive train with each of the drive trains including an endless drive belt which, in use, rotates the rotatable shaft components in it.
  • the rotatable shaft components are sprockets and the endless belt may be a chain which is engaged with the sprocket teeth.
  • the rotatable means on the extended ratio range input and output shafts and the clutch elements of both drive trains may be gears which are gear rotated by further meshed gears in a gear drive train.
  • the primary transmission may be a sequentially operable incremental CVT.
  • the primary transmission could be any suitable transmission or transmission system.
  • FIG. 1 is a basic schematic diagram which illustrates the operation of the invention
  • Figure 2 is a graph illustrating the operation of the extended transmission arrangement of the invention
  • FIGS 3 and 4 are identical block diagrams which together illustrate the operation of the transmission ratio extension of the invention
  • Figures 5 and 6 are isometric views from above and one side of the basic components of a practical example of the ratio extension arrangement of the invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
  • FIG. 1 illustrates the basic concept of the extended transmission ratio range arrangement of this invention.
  • the drawing shows a primary transmission, which in this example of the invention, is a sequentially operable CVT 10 and, for the purpose of explanation only, an imaginary dotted image 12 of the CVT 10 which is arranged with its low ratio end in a back-to-back relationship with the CVT 10.
  • the CVT 10 has, as shown in the drawing, a normal ratio range through gears 1 to 32 while the extended ratio range of the imaginary CVT 12 is through extended gears 33 to 64.
  • the normal ratio range A of the CVT 10 is illustrated in the Figure 2 graph where, assuming a constant input speed of rotation, it is shown that the ratio sequentially decreases in substantially uniform steps from gear number one at the beginning of the normal ratio range of CVT 10 to the normal range gear number 32.
  • next gear is switched from gear number 32, as shown in Figure 1 , to the imaginary CVT 12 extended gear number 33, as seen in the Figure 2 graph B, and from there through the extended dotted line gear range of the machine in an increase (1/the ratios of the CVT10) to its transmission gear number 64.
  • FIG. 3 and 4 An example of the ratio range extension arrangement of the invention is shown in Figures 3 and 4 to each comprise a primary transmission CVT 10, a first fixed gearing drive train 14(a) and 16(a), a second fixed gear drive train 14(b) and 16(b) and clutches 18, 20, 22 and 24. These components are connected as shown in the two diagrams with the arrangement additionally including a power input 26 from a prime mover and an output 28 to whatever is to be driven by the transmission.
  • Figure 3 illustrates, by means of the solid line arrows, a first linear power path through the conventional unextended ratio arrangement of the CVT 10 and Figure 4 the extended range dotted line arrow linear power path through the CVT 10.
  • FIGs 5 and 6 illustrate the practical essentials of the Figures 3 and 4 CVT 10 together withrits ratio range extension arrangement.
  • the fixed gearing drive train arrangements 14(a) and 14(b) and 16(a) and 16(b) are shown as composite first input and second output fixed gearing drive train arrangements 14 and 16 respectively.
  • the first drive train arrangement 14 is shown in Figures 4 and 5 to be composed of an input drive sprocket 30, two sprockets 32 and 34 and an endless chain 36 which drives the sprockets 32 and 34 from the input drive sprocket 30.
  • the second drive train arrangement 16 includes a power output sprocket 38, two sprockets 40 and 42 and an endless chain 44 which concomitantly drives the sprockets.
  • the input to the CVT is through a rotatable input shaft 46 and the CVT power output through an output shaft 48.
  • the sprockets 34 and 42 as well as the sprockets 32 and 40 are freely rotatable in fixed positions on the CVT 10 shafts 46 and 48.
  • the shafts are splined over their lengths between the sprockets which they carry.
  • Dog clutch components 50 and 52 are slidably located on the splined portions of the CVT shafts 46 and 48.
  • the sides of the sprockets 32, 34, 40 and 42 which face the dog clutch components 50 and 52 carry dog teeth which are engageable with those of the dog clutch components.
  • the sprocket 34 together with the clutch component 50 defines the clutch 18 of Figures 3 and 4 with the remaining clutches being defined in the drawings as follows: clutch 20 by the sprocket 40 and clutch member 52, clutch 22 by the sprocket 32 and the clutch member 52 and clutch 24 by the sprocket 42 and the clutch member 50.
  • the two clutch components 50 and 52 are switched from one sprocket to the other on the shafts which carry the components between their positions shown in Figures 4 and 5 on the transmission being shifted from the gear 32 to 33 by any suitable electric, hydraulic or pneumatic high speed switching arrangement.
  • Table 1 provides the ratios of the primary transmission CVT10, defined as the speed of input shaft 46 rotation divided by the speed of rotation of the output shaft 48 through each of the 32 ratios of the CVT 10, as shown in the left hand gear column, during normal operation of the CVT.
  • the extended gear ratios 33 to 64 are shown in the second gear column wherein the linear power path through the CVT 10 is reversed and the ratios are defined as the speed of the output shaft 48 rotation divided by the speed of rotation of the input shaft 46 and therefore 1 /(normal ratio) to conform to the reversed direction of linear power path flow through the CVT in its extended mode of operation.
  • the range extended transmission system includes a first non-extended linear power path through the transmission from the power input 26 to the power output 28 as illustrated in Figures 3 and 5 and in a reversed direction second linear power path between the input and output as illustrated in Figures 4 and 6.
  • the ratio range of the CVT 10 may sequentially be doubled in number but raised to the power of 2 in range by selecting the sizes of all of the sprocket gears in such a way that when the CVT 10 is in gear number 32 while transmitting power through the first linear power path ( Figures 3 and 5) the overall ratio (rpm of input sprocket 30 divided by the rpm of the output sprocket 38) will be substantially the same when transmitting power through the extended second linear power path ( Figures 4 and 6).
  • the rpm of sprockets 32 and 40 and sprockets 42 and 34 are likewise substantially the same during power transmission through the two linear power paths when the CVT is in gear number 32 and shifts to gear number 33 which facilitates almost instantaneous engagement of the dog clutch components with the relatively slowly rotating sprockets with which they are engageable without imposing shock loads on the clutch components or causing a perceptible interruption of power flow through the system.
  • Existing friction-based CVT's may also benefit from the range extension arrangement of the invention by being employed as the prime transmission of the system of this invention.
  • an existing belt and pulley CVT may be operated in such as way that the chain or belt only operates on larger radii on the conical surfaces where the torque capabilities and efficiencies are higher.
  • the resultant drop in ratio range (typically the square root of the normal ratio) can then be extended via the range extension method of this invention, back through the original CVT ratio range in a reverse direction.
  • the invention is not limited to the precise details as herein described.
  • the sprockets and chains of the first and second drive trains 14 and 16 of Figures 5 and 6 could be replaced by meshed gears and the dog clutch arrangements could be replaced by multiple plate clutches.
  • the primary transmission need not necessarily be that described in our WO2005/036028 publication and could be any suitable transmission or transmission system.

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

Abstract

L'invention porte sur un procédé d'extension de la plage des rapports d'une transmission primaire comportant les étapes suivantes: appliquer le couple moteur à la transmission primaire dans une première phase linéaire de puissance; monter normalement les vitesses de la transmission primaire du premier rapport au dernier; inverser le sens de la phase linéaire de puissance par une extension de la plage des rapports dans une deuxième phase linéaire de puissance de la transmission primaire; descendre les vitesses du dernier rapport au premier rapport; et ajouter les vitesses de la plage des rapports inverses à la plage des rapports normaux pour obtenir un plage étendue des rapports de la transmission primaire, dans le même sens que la plage normale des rapports de la transmission primaire.
PCT/ZA2006/000100 2005-09-09 2006-08-14 Extension de la plage des rapports d'une transmission WO2007030840A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ZA2005/07254 2005-09-09
ZA200507254 2005-09-09

Publications (1)

Publication Number Publication Date
WO2007030840A1 true WO2007030840A1 (fr) 2007-03-15

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PCT/ZA2006/000100 WO2007030840A1 (fr) 2005-09-09 2006-08-14 Extension de la plage des rapports d'une transmission

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WO (1) WO2007030840A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1020745A3 (nl) * 2012-06-06 2014-04-01 Punch Powertrain Nv Verbeterde continu variabele transmissie.

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE740071C (de) * 1934-12-05 1943-10-11 Piv Antrieb Reimers Kg Werner Getriebeanordnung
DE879350C (de) * 1951-04-28 1953-06-11 Patentverwertung W Reimers G M Stufenlos regelbares Getriebe
FR2303206A1 (fr) * 1975-03-04 1976-10-01 Scientific Res Foundation Systeme de transmission variable
FR2520826A1 (fr) * 1982-01-29 1983-08-05 Renault Transmission a variateur a deux modes de fonctionnement
DE3344042A1 (de) * 1983-12-06 1985-06-27 Claas Ohg, 4834 Harsewinkel Stufenloses getriebe
EP0210053A2 (fr) * 1985-07-22 1987-01-28 Borg-Warner Corporation Transmission continue à deux voies avec variateur asymétrique
DE4119291A1 (de) * 1991-06-12 1992-12-17 Hoehn Bernd Robert Prof Dr Ing Stufenloses getriebe
DE19631072A1 (de) * 1996-08-01 1998-02-05 Zahnradfabrik Friedrichshafen Wechselgetriebe für den Antrieb eines Fahrzeuges

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE740071C (de) * 1934-12-05 1943-10-11 Piv Antrieb Reimers Kg Werner Getriebeanordnung
DE879350C (de) * 1951-04-28 1953-06-11 Patentverwertung W Reimers G M Stufenlos regelbares Getriebe
FR2303206A1 (fr) * 1975-03-04 1976-10-01 Scientific Res Foundation Systeme de transmission variable
FR2520826A1 (fr) * 1982-01-29 1983-08-05 Renault Transmission a variateur a deux modes de fonctionnement
DE3344042A1 (de) * 1983-12-06 1985-06-27 Claas Ohg, 4834 Harsewinkel Stufenloses getriebe
EP0210053A2 (fr) * 1985-07-22 1987-01-28 Borg-Warner Corporation Transmission continue à deux voies avec variateur asymétrique
DE4119291A1 (de) * 1991-06-12 1992-12-17 Hoehn Bernd Robert Prof Dr Ing Stufenloses getriebe
DE19631072A1 (de) * 1996-08-01 1998-02-05 Zahnradfabrik Friedrichshafen Wechselgetriebe für den Antrieb eines Fahrzeuges

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1020745A3 (nl) * 2012-06-06 2014-04-01 Punch Powertrain Nv Verbeterde continu variabele transmissie.

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