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WO2016007034A1 - Transmission à variation continue à plages de rapport pouvant changer sous la charge - Google Patents

Transmission à variation continue à plages de rapport pouvant changer sous la charge Download PDF

Info

Publication number
WO2016007034A1
WO2016007034A1 PCT/RO2014/000030 RO2014000030W WO2016007034A1 WO 2016007034 A1 WO2016007034 A1 WO 2016007034A1 RO 2014000030 W RO2014000030 W RO 2014000030W WO 2016007034 A1 WO2016007034 A1 WO 2016007034A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
transmission
shaft
continuously variable
under load
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/RO2014/000030
Other languages
English (en)
Inventor
Nelu VASILICĂ
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 WO2016007034A1 publication Critical patent/WO2016007034A1/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
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
    • 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
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by parallel flow paths, e.g. dual clutch transmissions
    • 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
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H37/0846—CVT using endless flexible members
    • 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
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/0866—Power-split transmissions with distributing differentials, with the output of the CVT connected or connectable to the output shaft
    • F16H2037/0873—Power-split transmissions with distributing differentials, with the output of the CVT connected or connectable to the output shaft with switching means, e.g. to change ranges
    • 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
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power-split transmissions with summing differentials, with the input of the CVT connected or connectable to the input shaft
    • F16H2037/0886—Power-split transmissions with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges

Definitions

  • the invention refers to a continuously variable transmission that can change the gear ranges under load, designed to be used on transport means as well as on mobile or stationary equipment.
  • the technical problem solved by the invention is to provide a continuously variable transmission that can change the gear ranges with gear ratios arranged in arithmetic progression, without load interruption.
  • the continuously variable transmission with the change of gear ranges under load includes a drive shaft involving a power split input, which divides the power to two shafts connected to a speed variator, thus obtaining a differential variation of the speed for these two shafts, driving the inputs of two power splits, which have the united outputs with the output shaft of the transmission, and all the other inputs of the power splits are driven by the drive shaft via an intermediate transmission that can successively change the gear ranges, without the interruption of the torque moment.
  • Fig.l the basic diagram of the continuously variable transmission with gear ranges shiftable under load with hydrostatic variator
  • Fig.2 basic diagram of the continuously variable transmission with intermediate double clutch transmission and variator with variable pulleys and trapezoidal belt;
  • Fig.3 a functional diagram of the transmission in Fig.l;
  • Fig.4 a functional diagram of the transmission in Fig.2.
  • a continuously variable transmission which can change the gear ranges, without interrupting the load.
  • it consists of the drive shaft 1, involving the power split input D, which divides the power to shafts 6 and 7, connected to the hydrostatic variator VI, where it is obtained a differential variation of the speed at shafts 6, 7, which at their turn drive the ring gears 36, 37 of the power splits SI, S2 which have their outputs joint with the output shaft 25 of the transmission, and the sun gears 26, 27, of the power splits are driven by the secondary shafts 16, 17, of the intermediate transmission Tl.
  • the power split D having the role of dividing the power from the drive shaft 1 to shafts 6 and 7, consists of art planetary carrier 2, where are located some planetary gears 3, which are driven with the sun gear 4 and with the internal teeth of the ring gear 5, which has also external teeth which drive the shaft 6, by means of the gear wheel 8, joint with the intermediate shaft 9, on which is situated a gear wheel 10 and gear wheel 11 joint with shaft 6.
  • the variator VI is a hydrostatic converter, serving to impose a differential speed variation in shafts 6 and 7, it is composed of variable flow pump 18 connected to the shaft 6 and the variable flow hydraulic motor 19 connected to shaft 7, both pump 18 as well as hydraulic motor 19 have reversible functions and are connected to one another by means of a hydraulic circuit 20.
  • the power split SI serves at summing up the rotation speed of shaft 6 with the rotation speed of shaft 16 and to transmit it to the output shaft 25.
  • This one is composed of a sun gear 26 directly connected to shaft 16, some planetary gears 22, situated on the planetary carrier 24 which is common for both power splits and makes the connection with the output shaft 25, a ring gear 36 with internal teeth meshing the planetary gears 22 and external teeth driven by shaft 6 with the help of the gear wheel 12.
  • the power split S2 serves at summing up the rotation speed of shaft 7 with the rotation speed of shaft 17 and to transmit it to the output shaft 25.
  • This one is composed of the sun gear 27 fixed on shaft 17, planetary gears 23 located on the planetary carrier 24 and the ring gear 37 which is driven by the gear wheel 13, located on shaft 7.
  • the intermediate transmission Tl has the primary shaft common with the drive shaft 1 and drives both secondary shafts 16 and 17, by means of sets of gear wheels with the gear ratios arranged in arithmetic progression.
  • the first gear range is obtained by the action of the brake element a, on disk 15 joint with the secondary shaft 16.
  • Range II is obtained by using the gear wheel 30 joint with drive shaft 1, which drives the gear wheel 31 which makes the connection with secondary shaft 17, by means of clutch b.
  • Range III is obtained by means of the gear wheel 32, fixed on the drive shaft 1, driving the gear wheel 33 and makes connection with the secondary shaft 16 by means of clutch c.
  • Range IV is obtained by means of the gear wheels 34, fixed on the shaft 1, driving the gear wheel 35, which makes the connection with secondary shaft 17, by means of clutch d.
  • Fig. 2 is represented a variant of the continuously variable transmission with intermediate double clutch transmission and variator speed with variable pulleys and trapezoidal belt. This is composed of power split D and the power splits SI, S2, as well as the transmission in Fig. 1, the exception being the intermediate transmission T2 and variator V2, described below.
  • the intermediate transmission T2 comprises a double clutch housing 43, joint with drive shaft 1, composed of the friction clutch Al and A2, which contain the disks 44 and 45, which make the connection with the primary shafts 46, respectively 47, driving the secondary shafts 16 and 17, by means of sets of gear wheels, with gear ratios arranged in arithmetic progression.
  • Range I is implemented by coupling clutch Al and gear wheel 48 fixed on the primary shaft 46, driving a gear wheel 49 located on the intermediate shaft 50, on which is located a gear wheel 51, in its turn driving gear wheel 52, which is coupled with secondary shaft 16, by means of the coupling sleeve 53.
  • Range II is obtained by operating clutch A2, at which the gear wheel 54 joint with primary shaft 47, drives gear wheel 55 which is coupled with secondary shaft 17, by means of the coupling sleeve 56.
  • Range III is obtained operating clutch Al and the gear wheel 57 joint with primary shaft 46, drives gear wheel 58 which is coupled with the secondary shaft 16, by means of the coupling sleeve 53.
  • Range IV is obtained by operating clutch A2, at which the gear wheel 59 joint with the primary shaft 47, drives the gear wheel 60, which is coupled with the secondary shaft 17, by means of coupling sleeve 56.
  • the variator speed V2 is composed of variable pulley 38 joint with shaft 7, a trapezoidal belt 40 and the other variable pulley 39 joint with shaft 41, which is driven with shafts 9 and 6, by means of gear wheels 42, 10 and 11.
  • variable pulleys 38 and 39 is obtained a differential variation of the speed in shafts 6 and 7.
  • FIG. 3 and Fig. 4 are represented the functional diagrams of transmissions from Fig. 1 and Fig. 2, where:
  • vl is the tangential speed of the sun gear 26, when range I is coupled,
  • v3 is the tangential speed of the sun gear 26, when range III is coupled
  • v4 is the tangential speed of the sun gear 27, when range IV is coupled.
  • v36 At the moment tO, v36 is zero, the brake element a is operated, then vl is zero and it results coo equal to zero, v36 starts to increase until the maximum value., then the transmission reaches the moment tl and the angular speed of the output shaft 25 will be cool. At that moment v37 having the value zero the clutch b will be coupled, the transmission can operate with the two ranges simultaneously coupled until a steady coupling of clutch b is ensured, then the brake element a is released. v37 can start to increase, until the maximum value, when moment t2 is reached, and the angular speed of the output shaft 25 is coo2.
  • the variator V2 may impose a differential variation of tangential speeds v36 and v37, with values between minimum and maximum, and the intermediate transmission T2, is designed so that tangential speeds: -vl, v2, v3, v4 which are obtained at sun gears 26 and 27, are arranged in arithmetic progression, with the ratio equal to the difference between maximum and minimum value of v36, v37.
  • v36 has the minimum value
  • sleeve 53 is coupled with the gear wheel 52, gear range I having the transmission ratio so that vl is equal and opposite to v36min
  • clutch Al is coupled and result the angular speed of the output shaft 25, ⁇ is equal to zero.
  • the speed v36 starts to increase until the maximum value, then transmission reaches moment tl, thus resulting the angular speed ⁇ at the output shaft 25, at that moment v37, has the minimum value
  • sleeve 56 is coupled with gear wheel 55, clutch A2 is operated, then clutch Al and sleeve 53 is released.
  • v37 can start to increase, until the maximum value and moment t2 is reached, thus resulting the speed ⁇ 2 at the output shaft 25.
  • sleeve 53 is coupled with the gear wheel 58, clutch Al is coupled, then clutch A2 and sleeve 56 are released.
  • the increase of v36 may start, until the maximum value, moment t3 is reached and results the angular speed ⁇ 3 at the output shaft 25.
  • clutch 56 is coupled with the gear wheel 60, clutch A2 is operated, then clutch Al and sleeve 53 is released, after which can start the increase of v37, until the maximum value, when transmission reaches moment t4 and results the angular speed too4 at the output shaft 25.

Landscapes

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

Abstract

L'invention fait référence à une transmission variable continue qui peut changer les plages de rapport des rapports de transmission agencés en progression arithmétique, sans interruption de la charge. Selon l'invention, la transmission se compose d'un diviseur de puissance (D), entraîné par l'arbre d'entraînement (1) qui divise la puissance vers des arbres (6) et (7) reliés à un variateur de vitesse (V1) et entraînant les couronnes dentées (36), (37) des diviseurs de puissance (S1), respectivement (S2), qui ont un arbre de sortie commun (25). Les planétaires (26), (27) sont entraînés par l'arbre d'entraînement (1) au moyen d'une transmission (T1).
PCT/RO2014/000030 2014-07-10 2014-11-04 Transmission à variation continue à plages de rapport pouvant changer sous la charge Ceased WO2016007034A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ROA201400529A RO129945A0 (ro) 2014-07-10 2014-07-10 Transmisie variabilă continuă cu schimbarea gamelor de turaţie în sarcină
RO201400529 2014-07-10

Publications (1)

Publication Number Publication Date
WO2016007034A1 true WO2016007034A1 (fr) 2016-01-14

Family

ID=52007251

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/RO2014/000030 Ceased WO2016007034A1 (fr) 2014-07-10 2014-11-04 Transmission à variation continue à plages de rapport pouvant changer sous la charge

Country Status (2)

Country Link
RO (1) RO129945A0 (fr)
WO (1) WO2016007034A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3675507A (en) * 1969-10-03 1972-07-11 Takekawa Iron Works Hydraulic transmission mechanism for heavy rolling stocks and the like
WO1994015121A1 (fr) * 1992-12-23 1994-07-07 J.C. Bamford Excavators Limited Transmission variable en continu, a division de puissance et multi-etagee
US20050059521A1 (en) * 2003-09-16 2005-03-17 Komatsu Ltd. Control system for a hydro-mechanical transmission
WO2009047035A1 (fr) * 2007-10-02 2009-04-16 Zf Friedrichshafen Ag Dispositif de transmission avec un variateur
DE102008001326A1 (de) * 2008-04-23 2009-10-29 Zf Friedrichshafen Ag Stufenlose Getriebevorrichtung eines Antriebsstranges eines Fahrzeuges

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3675507A (en) * 1969-10-03 1972-07-11 Takekawa Iron Works Hydraulic transmission mechanism for heavy rolling stocks and the like
WO1994015121A1 (fr) * 1992-12-23 1994-07-07 J.C. Bamford Excavators Limited Transmission variable en continu, a division de puissance et multi-etagee
US20050059521A1 (en) * 2003-09-16 2005-03-17 Komatsu Ltd. Control system for a hydro-mechanical transmission
WO2009047035A1 (fr) * 2007-10-02 2009-04-16 Zf Friedrichshafen Ag Dispositif de transmission avec un variateur
DE102008001326A1 (de) * 2008-04-23 2009-10-29 Zf Friedrichshafen Ag Stufenlose Getriebevorrichtung eines Antriebsstranges eines Fahrzeuges

Also Published As

Publication number Publication date
RO129945A0 (ro) 2014-12-30

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