WO2004083686A1 - Poulie entrainee pour transmission a variation continue - Google Patents

Poulie entrainee pour transmission a variation continue Download PDF

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Publication number
WO2004083686A1
WO2004083686A1 PCT/CA2004/000401 CA2004000401W WO2004083686A1 WO 2004083686 A1 WO2004083686 A1 WO 2004083686A1 CA 2004000401 W CA2004000401 W CA 2004000401W WO 2004083686 A1 WO2004083686 A1 WO 2004083686A1
Authority
WO
WIPO (PCT)
Prior art keywords
sheave
driven pulley
sleeve portion
ramps
ramp
Prior art date
Application number
PCT/CA2004/000401
Other languages
English (en)
Inventor
Jocelyn Labbe
Original Assignee
Cvtech R & D Inc.
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
Priority claimed from CA002422455A external-priority patent/CA2422455C/fr
Priority claimed from US10/389,832 external-priority patent/US6949039B2/en
Application filed by Cvtech R & D Inc. filed Critical Cvtech R & D Inc.
Publication of WO2004083686A1 publication Critical patent/WO2004083686A1/fr

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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
    • F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
    • F16H63/067—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions mechanical actuating means
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
    • F16H61/66272—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing

Definitions

  • Continuously variable transmissions are commonly used on a wide range of vehicles, such as small cars or trucks, snowmobiles, golf carts, scooters, etc. They typically comprise a driving pulley mechanically connected to a motor, a driven pulley mechanically connected to wheels or a track, possibly through another mechanical device such as a gear box, and a trapezoidal drivebelt transmitting torque between the driving pulley and the driven pulley.
  • a CVT automatically changes the ratio as required by load and speed conditions, providing an increased torque under high loads at low speeds and yet controlling the rotation speed of the motor as the vehicle accelerates.
  • a CVT may be used with all kinds of motors, such as internal combustion engines or electric motors.
  • the sides of the drivebelt are, on each pulley, gripped between two opposite sheaves that are coaxially mounted around a corresponding main shaft.
  • one sheave usually called “fixed sheave”
  • the other sheave usually called “movable sheave”
  • the winding diameter of the drivebelt at the driving pulley is minimal and the winding diameter of the driven pulley is maximum. This is referred to as the minimum ratio since there is the minimum number of rotations or fraction of rotation of the driven pulley for each full rotation of the driving pulley.
  • the cam system typically comprises a cam plate having a plurality of symmetrically- disposed and inclined ramps on which respective cam followers are engaged.
  • the followers are usually sliding buttons or rollers.
  • the set of ramps or the set of followers is mounted on the movable sheave and the other is directly or indirectly connected to the main shaft in a rigid manner. The closing effect of the cam system on the drivebelt tension is then somewhat proportional to output torque.
  • the ratio is maximum as there is the maximum number of rotations or fraction of rotation of the driven pulley for each full rotation of the driving pulley. Then, when the vehicle speed decreases, the rotation speed of the driving pulley typically decreases as well since the rotation speed of the motor decreases. This causes, at some point, a decrease of the winding diameter of the driving pulley and a decrease of the radial force exerted by the drivebelt on the sides of the sheaves at the driven pulley. Ultimately, the driven pulley is allowed to have a larger winding diameter as the spring or another biasing mechanism moves the movable sheave back towards the fixed sheave.
  • a reversible driven pulley operates in a similar fashion than that of a conventional one, with the exception that the transmission ratio can be controlled during motor braking or when the vehicle is traveling in reverse. For instance, during motor braking, the torque is no longer coming from the motor to the wheels or track, but in the opposite direction. Similarly, when accelerating in reverse, the torque and the rotation will be in the reverse direction, the torque being transmitted from the motor to the wheels or track.
  • a reversible driven pulley generally comprises a second set of ramps and a second set of followers. In use, one set of followers and its corresponding set of ramps are used when the torque is in one direction, the other set being used for the other direction.
  • a common problem to most driven pulleys is that they tend to be heavy and cumbersome, especially in applications where a high torque is transmitted. There was thus a need to provide a driven pulley having a new configuration and design which allows a more compact and efficient design.
  • a driven pulley for use on a main shaft defining a rotation axis.
  • the driven pulley is characterized in that it comprises: a first sheave having a first side and a second side, the first sheave comprising: a substantially annular and radially-extending main portion, the main portion having a conical wall provided on the first side of the first sheave; a substantially axially-extending bracket portion connected to the main portion and projecting from the second side of the first sheave, the bracket portion defining an internal enclosure opened at the first side of the first sheave; a sleeve portion connected to the bracket portion at a distal location with reference to the main portion; and - at least two ramps symmetrically-disposed with reference to the rotation axis and connected to the first sheave inside the internal enclosure; a second sheave having a first side and a second side, the second sheave comprising: a substantially annular and radially-extending main portion, the main portion of
  • the outer sleeve portion of the second sheave is housed in the internal enclosure of the first sheave and each follower is configured and disposed for being in engagement with a corresponding ramp, the sleeve portion of the first sheave being rigidly connected to the main shaft while the inner sleeve portion of the second sheave being free to rotate and slide with reference to the main shaft.
  • FIG. 1 is an exploded view of a driven pulley in accordance with a preferred embodiment of the present invention
  • FIG. 2 is a cross-section view of the driven pulley shown in FIG. 1 , the upper half showing the pulley at a low ratio position and the lower half showing the pulley at a high ratio position;
  • FIG. 3 is a perspective view of the second side of the first sheave shown in FIG. 1 ;
  • FIG. 4 is a perspective view of the first side of the second sheave shown in
  • FIG. 1 is an enlarged view showing an example of a double-sided sliding button
  • FIG. 6 is an enlarged view illustrating the double-sided sliding button between a pair of corresponding ramps
  • FIG. 7 is an exploded view of the second sheave with removable ramps
  • FIG. 8 is a view similar to FIG. 6, illustrating the double-sided sliding button in contact with a removable ramp;
  • FIG. 9 is a top perspective view of a removable ramp.
  • FIG. 10 is a bottom perspective view of the removable ramp of FIG. 9.
  • FIGS. 1 to 6 there is shown an example of a driven pulley (10) according to a preferred embodiment of the present invention. It is to be understood that the present invention is not limited to this precise embodiment and that various changes and modifications may be effected therein without departing from the scope or spirit of the present invention.
  • the driven pulley (10) is mounted on a main shaft (not shown) which defines a rotation axis.
  • main shaft not shown
  • single parts of the driven pulley (10) are coaxially mounted around the rotation axis and multiples of a same part are symmetrically disposed around it in order to have a properly-balanced device, as apparent to a person skilled in art.
  • the torque is transmitted to or from the main shaft by the driven pulley (10).
  • This torque is supplied from or to a trapezoidal drivebelt (not shown).
  • the trapezoidal drivebelt has one end wound on a driving pulley (not shown) and the other end wound on the driven pulley (10), more particularly around a first (12) and a second sheave (40).
  • the torque usually goes from the driven pulley (10) to the main shaft.
  • the driven pulley (10) is reversible, the torque can be transmitted in the opposite direction
  • the first sheave (12) has a first side (14) and a second side (16). Most portions of the first sheave (12), if not all, are part of a one-piece aluminum die-cast or the like. These portions are thus integrally-connected together.
  • the first portion is a substantially annular and radially-extending main portion (20).
  • the main portion (20) has a conical wall (22) provided on the first side (14) of the first sheave (12) and is designed to engage one side of the trapezoidal drivebelt.
  • the first sheave (12) further comprises a substantially axially-extending bracket portion (30) connected to the main portion (20) and projecting from the second side (16) of the first sheave (12).
  • the bracket portion (30) generally defines an internal enclosure (32) opened at least at the first side (14) of the first sheave (12).
  • the back of the bracket portion (30) is preferably provided with a plurality of reinforcing ribs (31 ).
  • the first sheave (12) also comprises a sleeve portion (34) connected to the bracket portion (30) at a distal location with reference to the main portion (20).
  • the sleeve portion (34) has a central hole (35) allowing the main shaft to be inserted therein.
  • the sleeve portion (34) acts as a connection point between the driven pulley (10) and the main shaft. This allows the torque to be transmitted between them. This connection may be achieved in a number of ways.
  • the driven pulley (10) is rigidly connected to the main shaft by a mounting tube (38) which is to be coaxially-mounted over the main shaft.
  • the mounting tube (38) has one end rigidly connected to the perimeter of the hole (35) of the sleeve portion (34).
  • the main shaft also has a hollow interior in which the main shaft can be tightly inserted.
  • Retention means for instance a spline, a screw, internal teeth, etc. provide the torque-transmitting engagement, as apparent to a person skilled in the art.
  • the mounting tube (38) can also be retained by welding, glue, etc. The length of the mounting tube (38) must be sufficient for allowing its free end to extend beyond the second sheave (40). This way, the mounting tube (38) can be used as a base for the second sheave (40) and the other parts.
  • the driven pulley (10) can then be assembled in advance and simply fitted into place on the main shaft.
  • the first sheave (12) further comprises at least one or two pairs of ramps (36), depending if the driven pulley (10) is reversible or not.
  • the ramps (36) are preferably provided near the side openings (33).
  • the ramps (36) are symmetrically-disposed with reference to the rotation axis and connected to the first sheave (12) inside the internal enclosure (32).
  • two sets of ramps (36) are provided.
  • FIG. 6 shows the relative position of the two ramps (36) of a same set in the preferred embodiment. One will be for the forward direction, the other being for the reverse direction.
  • the ramps (36) of the first set are not necessarily identical to those of the second set.
  • the driven pulley (10) further comprises a second sheave (40) having a first side (42) and a second side (44).
  • the second sheave (40) can be in the form of a one-piece item or be made of a plurality of parts secured together.
  • the second sheave (40) has a substantially annular and radially-extending main portion (50).
  • the main portion (50) of the second sheave (40) has a conical wall (52) on its first side (42).
  • the conical wall (52) is preferably identical to the conical wall (22) provided on the first sheave (12).
  • the second sheave (40) also comprises an outer sleeve portion (60) axially projecting from the first side (42) of the second sheave (40), as shown in FIG. 4.
  • the outer sheave portion (60) is sized to fit into the internal enclosure (32) of the first sheave (12) once the driven pulley (10) is assembled.
  • An inner sleeve portion (62) is coaxially positioned inside the outer sleeve portion (60).
  • the inner sleeve portion (62) has a smaller outer diameter than the inner diameter of the outer sleeve portion (60) so as to define between them an annular space (64) with a substantially closed bottom.
  • the inner sleeve (62) comprises bushings (66) or the like on the interior side thereof. This allows the second sheave (40) to slide and rotate with reference to the main shaft, thus moving relative of the first sheave (12).
  • the bushings (66) can be in engagement with the main shaft directly.
  • the second sheave (40) is mounted on the mounting tube (38) and consequently, the bushings (66) are in sliding and rotational engagement with the mounting tube (38).
  • the bushings (66) can be replaced by an equivalent, such as bearings or the like.
  • the inner sleeve portion (62) slightly extends from the end of the outer sleeve portion (60). This provides a stop for limiting the minimum spacing between the first (12) and the second sheave (40). This is however optional.
  • Followers (70) and corresponding mounting supports (72) are symmetrically disposed on the outer sleeve portion (60). Each follower (70) can be in the form of a sliding button, a roller or the like, depending on the needs.
  • the mounting supports (72) are configured and disposed to allow each follower (70) to engage a corresponding ramp (36).
  • Each mounting support (72) projects radially from the outer sleeve portion (60) and comprises a clamp (74) where the follower (70) is installed.
  • the followers (70) are installed in the clamps (74) and a screw (76) or another retaining means is used to fully maintain the follower (70) in place, as shown in FIG. 1.
  • the size of the internal enclosure (32) must be such that the outer sleeve portion (60) and the mounting supports (72) can be inserted therein.
  • the mounting supports (72) are projecting out of side openings (33) when the second sheave (40) is in place. This provides two main advantages. The first is that the internal enclosure (32) can be smaller when the mounting supports (72) are allowed to move within the side openings (33). The other advantage is that the followers (70) can be inspected and replaced without the need of disassembling the driven pulley (10).
  • the second side (44) of the second sheave (40) is provided with a plurality of reinforcing ribs (46), as shown in FIG. 2.
  • the driven pulley (10) comprises an axially-disposed helical spring (80) having one end resting against a fixed point at the closed bottom of the annular space (64) and an opposite end connected to a fixed location with reference to the first sheave (12).
  • the fixed end of the spring (80) rests against an optional protector (82), itself resting on a stop (84) held by a C-clip (86) or another means connected to the mounting tube (38).
  • the spring (80) is pre-loaded in compression and/or in torque, depending on the needs.
  • the purpose of the spring (80) is to create a return force urging the second sheave (40) towards the first sheave (12).
  • the spring (80) can be pre-loaded in torque, with or without a pre-load in compression, so as to force the followers (70) to move up the ramps (36). This also forces the second sheave (40) to move closer to the first sheave (12).
  • the outer sleeve portion (60) of the second sheave (40) is housed in the internal enclosure (32) of the first sheave (12).
  • Each follower (70) of a same set engages a corresponding ramp (36).
  • the torque, if transmitted from the drivebelt, has one half going through the first conical wall (22) and a second half going through the second conical wall (52).
  • the torque in the first sheave (12) is directly transmitted to the main shaft by the bracket portion (30), the sleeve portion (34) and then the optional mounting tube (38).
  • the other half of the torque, in the second sheave (40) is transmitted to the outer sleeve portion (60), the mounting supports (72) and then the followers (70).
  • the followers (70) transmit the torque in their turn to the ramps (36), that being added to the first torque half and following the same path.
  • doubled-sided sliding buttons (70) can be provided, each side of the follower being capable of engaging a corresponding ramp (36).
  • An example of a double-sided sliding button (70) is shown in FIG. 5. As shown in FIG. 6, one side of the sliding button (70) can engage one ramp (36) while the other can engage the opposite ramp (36).
  • the driven pulley (10) will go through a short transition when the torque changes direction. In that case, the second sheave (40) will slightly rotate with reference to the first sheave (12), thereby changing the side of the sliding button (70) and the set of ramps (36) being used.
  • the present invention allows the driven pulley (10) to be constructed in very compact manner and consequently with a smaller weight compared to an equivalent conventional driven pulley.
  • Another advantage is that the followers (70) and the removable ramps (36'), if any, can be installed, inspected and replaced after the assembly of the driven pulley (10).
  • the ramps (36), or at least one set if there is more than one, are each removably connected to the first sheave (12) by means of a fastener, for instance a bolt (90).
  • a fastener for instance a bolt (90).
  • Other kinds of fasteners can be used as well.
  • the removable ramps, identified with reference numeral 36' are positioned in corresponding seats (92) of the first sheave (12). Once in position, the bolt (90) is inserted through a hole (94) made in the largest part of the removable ramp (36') and reaches a threaded hole (96) provided in the seat (92). It is tighten thereafter.
  • the hole (94) in the removable ramp (36') is located in a region where the follower (70) will not reach it.
  • FIG. 8 shows a removable ramp (36') against which a double-sided follower (70) is engaged.
  • the general operation of the driven pulley (10) remains unaffected by the presence of removable ramps (36') compare to integrated ramps (36).
  • FIGS. 9 and 10 show an individual removable ramp (36').
  • the ramp (36') features a plurality of side protrusions (98) designed to position the removable ramp (36') at the right location in its seat (92).
  • first sheave (12) for a given purpose without having to modify the first sheave (12) itself.
  • the same first sheave (12) can thus be used for different kinds of vehicles and with different settings.
  • the above-described and illustrated design further allows removing and installing the removable ramps (36') without having to remove the driven pulley (10) or its first sheave (12) from the vehicle.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmissions By Endless Flexible Members (AREA)
  • Pulleys (AREA)

Abstract

L'invention concerne une poulie entraînée (10) qui comprend une première gorge (12) et une seconde gorge (40) montées coaxiales autour d'un arbre principal. La première gorge (12) est fixe par rapport à l'arbre principal, et la seconde coulisse et tourne par rapport à lui. Cette poulie (10) est conçue pour qu'une partie de la seconde gorge (40) pénètre dans la première gorge (12). Un ressort de rappel (80) est prévu à l'intérieur de la poulie entraînée (10), laquelle peut être conçue comme poulie entraînée réversible par adjonction d'une seconde série de rampes (36) et de suiveurs (70). Il s'agit d'une poulie de configuration très compacte, et donc de poids inférieur par rapport à une poulie entraînée classique.
PCT/CA2004/000401 2003-03-17 2004-03-17 Poulie entrainee pour transmission a variation continue WO2004083686A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CA002422455A CA2422455C (fr) 2003-03-17 2003-03-17 Poulie d'entrainement pour transmission a changement de vitesses continu
CA2,422,455 2003-03-17
US10/389,832 2003-03-17
US10/389,832 US6949039B2 (en) 2003-03-17 2003-03-17 Driven pulley for a continuously variable transmission

Publications (1)

Publication Number Publication Date
WO2004083686A1 true WO2004083686A1 (fr) 2004-09-30

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ID=33030450

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CA2004/000401 WO2004083686A1 (fr) 2003-03-17 2004-03-17 Poulie entrainee pour transmission a variation continue

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WO (1) WO2004083686A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2162644A1 (fr) * 2007-06-08 2010-03-17 Cvtech R & D Inc. Poulie entrainee pour transmission a variation continue
CN112664639A (zh) * 2021-03-17 2021-04-16 华南新海(深圳)科技股份有限公司 一种传动带张紧装置及带传动***

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4403976A (en) * 1979-06-13 1983-09-13 Kawasaki Jukogyo Kabushiki Kaisha Clutch for belt drive
US6120399A (en) * 1998-06-11 2000-09-19 Product Research And Development, Inc. Continuously variable transmission driven element
US20020032088A1 (en) * 2000-09-01 2002-03-14 Norbert Korenjak Continuously variable transmission for an internal combustion engine
US20020065156A1 (en) * 1999-11-29 2002-05-30 Younggren Bruce H. Clutch with a one-way torque carrying bearing
EP1234128A1 (fr) * 1999-11-29 2002-08-28 CVTECH-IBC Inc. Poulie entrainee

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4403976A (en) * 1979-06-13 1983-09-13 Kawasaki Jukogyo Kabushiki Kaisha Clutch for belt drive
US6120399A (en) * 1998-06-11 2000-09-19 Product Research And Development, Inc. Continuously variable transmission driven element
US20020065156A1 (en) * 1999-11-29 2002-05-30 Younggren Bruce H. Clutch with a one-way torque carrying bearing
EP1234128A1 (fr) * 1999-11-29 2002-08-28 CVTECH-IBC Inc. Poulie entrainee
US20020032088A1 (en) * 2000-09-01 2002-03-14 Norbert Korenjak Continuously variable transmission for an internal combustion engine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2162644A1 (fr) * 2007-06-08 2010-03-17 Cvtech R & D Inc. Poulie entrainee pour transmission a variation continue
EP2162644A4 (fr) * 2007-06-08 2010-06-23 Cvtech R & D Inc Poulie entrainee pour transmission a variation continue
CN112664639A (zh) * 2021-03-17 2021-04-16 华南新海(深圳)科技股份有限公司 一种传动带张紧装置及带传动***
CN112664639B (zh) * 2021-03-17 2021-06-01 华南新海(深圳)科技股份有限公司 一种传动带张紧装置及带传动***

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