WO2016168439A1 - Serrage hydraulique centrifuge passif pour fonctionnement planétaire à variation continue à grande vitesse - Google Patents

Serrage hydraulique centrifuge passif pour fonctionnement planétaire à variation continue à grande vitesse Download PDF

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Publication number
WO2016168439A1
WO2016168439A1 PCT/US2016/027496 US2016027496W WO2016168439A1 WO 2016168439 A1 WO2016168439 A1 WO 2016168439A1 US 2016027496 W US2016027496 W US 2016027496W WO 2016168439 A1 WO2016168439 A1 WO 2016168439A1
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WIPO (PCT)
Prior art keywords
clamping
drive ring
clamping element
continuously variable
force
Prior art date
Application number
PCT/US2016/027496
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English (en)
Inventor
Robert A. Smithson
Michael P. FRINK
Patrick Sexton
Sebastian Peters
Andrew Phillips
Original Assignee
Dana Limited
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Publication of WO2016168439A1 publication Critical patent/WO2016168439A1/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
    • 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
    • F16H61/664—Friction gearings
    • F16H61/6649—Friction gearings characterised by the means for controlling the torque transmitting capability of the gearing
    • 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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/26—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution
    • F16H15/28—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution with external friction surface

Definitions

  • a vehicle having a driveline including a tilting ball variator allows an operator of the vehicle or a control system of the vehicle to vary a drive ratio in a stepless manner.
  • a variator is an element of a Continuously Variable Transmission (CVT) or an Infinitely Variable Transmission (IVT). Transmissions that use a variator can decrease the transmission's gear ratio as engine speed increases. This keeps the engine within its optimal efficiency while gaining ground speed, or trading speed for torque during hill climbing, for example. Efficiency in this case can be fuel efficiency, decreasing fuel consumption and emissions output, or power efficiency, allowing the engine to produce its maximum power over a wide range of speeds. That is, the variator keeps the engine turning at constant RPMs over a wide range of vehicle speeds.
  • a tilting ball variator (Continuously Variable Planetary - CVP) is a form of traction drive based on a planetary gearing principle.
  • a traction drive flat-surfaced rollers contact with other flat-surfaced rollers without teeth, and transfer power. This is accomplished using a lubricant called 'traction oil' or "traction fluid" to create an elasto-hydrodynamic film.
  • a CVP includes a first drive ring, a second drive ring, and a plurality of variator balls, also referred to as traction planets, disposed between the first drive ring and the second drive ring.
  • the plurality of traction planets is simultaneously tilted, which adjusts an axis angle of each of the traction planets, for example, by moving a carrier, on which the plurality of traction planets are rotatably disposed.
  • the plurality of traction planets are in driving engagement with the first drive ring and the second drive ring through one of a boundary layer type friction and an elasto-hydrodynamic film where the increased moment of inertia and weight of large traction planets decrease the effectiveness of the elasto-hydrodynamic boundary layer friction coupling between the traction planets and drive rings. Loss of effective frictional coupling leads to decreases in efficiency and performance of the overall CVT.
  • the invention pertains to devices and methods relating to generating clamping force in certain types of transmissions necessary to maintain effective passive frictional coupling between the traction planets and drive rings,
  • CVT and Infinitely Variable Transmissions often use some form of mechanical clamping mechanism, typically comprising a ball-and-cam mechanism to generate axial clamping forces necessary to facilitate the transmission of torque between or among transmission components via traction or friction, often referred to as clamping force mechanisms or generators.
  • clamping force mechanisms typically referred to as clamping force mechanisms or generators.
  • a standard ball-and-cam clamping force mechanism determines the clamp load.
  • Non-Torque Reactive a clamping force generator
  • Torque Reactive a clamping force generator
  • Active/Programmable a clamping force generator
  • Non-Torque Reactive clamping means are generally defined as ratio dependent, speed dependent and fixed (fully preloaded).
  • Torque Reactive clamping means are generally defined by axial forces due to: external influences or loads; torque reaction on floating elements; screws and cams; or passive hydraulic; and
  • Active/Programmable clamping means wherein hydraulic or other means are actively applied to a clamping means to create axial clamping forces.
  • the clamping force mechanism used in a transmission with a Continuously Variable Ball Planetary (CVP) variator provides a load to the input and/or output ring to ensure adequate clamping force between the drive ring(s) and the traction planets.
  • CVP Continuously Variable Ball Planetary
  • a continuously variable ball planetary transmission having passive centrifugal clamping means
  • the continuously variable ball planetary comprising: a plurality of tilting traction planets mounted on a carrier, the traction planets in contact with a first drive ring and a second drive ring and a traction fluid; at least one axial force mechanism in contact with at least one of the first drive ring or the second drive ring through one or more cam bearings; at least one enclosed rotating cavity optionally comprising bleed holes; at least one clamping element (a piston/ring), adjacent to and at least partially within the rotating cavity, in
  • the hydraulic pressure within the cavity generated by centrifugal force as a result of high rotational speeds of the continuously variable ball planetary, exerts pressure against the clamping element.
  • the hydraulic pressure applied to the clamping element is combined with a cam clamp load provided by the at least one axial force mechanism to apply axial loading to at least one of the first drive ring or the second drive ring to increase pressure against the tilting traction planets.
  • the increased axial force is applied to the first drive ring and/or second drive ring to counteract hydrodynamic lift between the tilting traction planets and the first drive ring and/or second drive ring.
  • a clamping element applies a variable hydraulic clamping force to at least one axial force mechanism.
  • the variable hydraulic clamping force is produced by centrifugal force generated by the hydraulic fluid exerted on the clamping element (piston/ring) resulting from a rotational speed of the clamping element .
  • the variable hydraulic clamping force is a squared function of the rotational speed of the clamping element.
  • the radial locations of the optional bleed holes in at least one enclosed, rotating cavity determines a gain of the clamping force with respect to the squared speed of the clamping element.
  • the cam bearing is configured for relative rotation with respect to the first drive ring, the relative rotation corresponding to an operating torque of the CVT, and wherein the bleed holes are arranged to be blocked by the cam bearing under high torque operation.
  • the cam bearing uncovers the bleed holes under low torque operation.
  • the clamping force is defined as: dp ,
  • F D clamping force
  • ⁇ angular velocity in radians/second
  • r 2 maximum radius of the piston face
  • ⁇ inner radius of the piston
  • R 0 inner radius of hydraulic fluid (bleed hole radius / exit radius of fluid
  • p fluid density
  • ⁇ mathematical constant.
  • Ro ⁇ .
  • the clamping force may be determined by other formulae comprising similar and /or different variables known to those skilled in the art.
  • the radial locations of the optional bleed holes are within a range of about 0.1 mm and 200.0 mm, 10.0 mm and 175.0 mm, 20.0 mm and 150.0 mm, 30.0 mm and 130.0 mm, 30.0 mm and 120.0 mm, 30.0 mm and 110.0 mm, 30.0 mm and 100.0 mm, 30.0 mm and 90.0 mm, 30.0 mm and 80.0 mm, 30.0 mm and 75.0 mm, 30.0 mm and 70.0 mm, 30.0 mm and 65.0 mm, 30.0 mm and 60.0 mm, 30.0 mm and 55.0 mm, 30.0 mm and 50.0 mm, 30.0 mm and 45.0 mm, 30.0 mm and 40.0 mm, 35.0 mm and 80.0 mm, 40.0 mm and 80.0 mm, 45.0 mm and 80.0 mm, 50.0 mm and 80.0 mm, 55.0 mm and 80.0 mm, 60.0 mm and 80.0 mm, 65.0 mm and 8
  • the number of the optional bleed holes is within about 0 and 30. In some embodiments, the bleed hole is inside the diameter of the piston. In some embodiments of the continuously variable ball planetary, the diameter of the optional bleed holes is within about 0.20 mm and 8.0 mm.
  • a method of generating passive centrifugal hydraulic clamping force in a continuously variable ball planetary comprising applying an additive passive centrifugal axial hydraulic clamping force to a first clamping element (piston/ring), at any rotational speed, causing the clamping element to engage a first axial force mechanism in contact with a first drive ring through a cam bearing.
  • the centrifugal clamping force applied by the first clamping element (piston/ring) is combined with a clamp load from the first axial force mechanism to increase pressure between the first drive ring and the rotating traction planets.
  • the centrifugal clamping force applied by the first clamping element is combined with a clamp load from a preload nut to increase pressure between the first drive ring and the rotating traction planets.
  • the continuously variable ball planetary is in overdrive.
  • the axial force mechanism is a cam.
  • the cam is single- sided, or double-sided.
  • the cam is uni-directional or bi-directional.
  • the axial force mechanism is a single cam (on the input or output ring) or a dual cam (on the input ring and output ring). In other embodiments the axial force mechanism is a roller load cam.
  • the clamping element is an axially sliding element, (e.g. : a stepped ring), in intimate, sealed contact with a rotating cavity having optional bleed holes positioned radially, adjacent the diametral face of the clamping element, and ideally in the approximate radial center of either a first or a second drive ring face, (in a single cam
  • the clamping element is immediately adjacent, to and in contact with the first or second drive ring through a cam bearing.
  • a cam bearing In some embodiments of a single cam
  • the clamping elements are axially sliding elements, (e.g.
  • a stepped ring in intimate, sealed contact with rotating cavities comprising optional bleed holes positioned radially, adjacent the diametral face of more two clamping elements, and ideally in the approximate radial center of both a first and a second drive ring face, (such as in a dual cam configuration).
  • the clamping elements are immediately adjacent, to and in contact with the first and second drive ring through a cam bearing.
  • a method of generating passive centrifugal hydraulic clamping force in a continuously variable ball planetary comprising applying an additive passive centrifugal axial hydraulic clamping force to a second clamping element (piston/ring), at rotational speed, causing the clamping element to engage an second axial force mechanism in contact with a second drive ring through a cam bearing.
  • the centrifugal clamping force applied by the second clamping element (piston/ring) is combined with a cam clamp load from the second axial force mechanism to increase pressure between the second drive ring and the rotating traction planets.
  • the centrifugal clamping force applied by the second clamping element (piston/ring) is combined with a cam clamp load from the second axial force mechanism to increase pressure between the second drive ring and the rotating traction planets.
  • a method of generating passive centrifugal clamping force between rotating traction planets and a first drive ring and a second drive ring for a continuously variable ball planetary comprising applying an additive passive centrifugal axial hydraulic clamping force to a first clamping element (piston/ring) and a second clamping element (piston/ring), at rotational speed, causing the first and second clamping elements to engage a first axial force mechanism and a second axial force mechanism in contact with the first drive ring and the second drive ring through cam bearings.
  • the centrifugal clamping force applied by the first clamping element (piston/ring) and the second clamping element (piston/ring) is combined with a system preload from the first axial force mechanism and the second axial force mechanism to increase pressure between the first drive ring, the second drive ring, and the rotating traction planets.
  • a side of the variator with higher revolutions per minute would be an active speed-dependent clamp side.
  • a non-active cam driver would react to the active clamp load and the pressure from the fluid within the variator to become the active cam driver.
  • the non-active cam is for example, ring 2, [assuming the system is in overdrive], and the input [Rl] is at a low torque state, and if the hydraulic clamp mechanism on R2 is producing a higher clamp force due to its speed, then it reacts to become the active clamp device.
  • the centrifugal clamping force is generated by hydraulic pressure applied to a clamping element, whereby said hydraulic pressure generates an additive force in excess of a cam clamp load generated by the first or second axial force mechanism, in the continuously variable ball planetary.
  • the combined clamping force of the clamping element and the axial force mechanism exceeds a predetermined value of the cam clamp load of a ball-and-cam axial force mechanism to produce a useful increase in total clamping force at low torque/high speed.
  • a continuously variable planetary transmission comprising a variator with passive centrifugal clamping means, the variator comprising: a plurality of tilting traction planets mounted on a carrier, the traction planets in contact with a first drive ring and a second drive ring; at least one axial force mechanism; at least one enclosed, rotating cavity ; at least one clamping element (piston/ring), adjacent to and at least partially within the rotating cavity, in approximate contact with the axial force mechanism and hydraulic fluid within the rotating cavity, wherein the hydraulic fluid is subject to centrifugal force as a result of rotational speeds of the continuously variable ball planetary; wherein at least one rotating cavity, generates hydraulic pressure at any rotational speeds and exerts a force on at least one clamping element adequate to fully engage at least one axial force mechanism, wherein the force generated on the first and/or second drive ring is greater than a torque controlled ramp force provided by at least one axial force mechanism alone.
  • a method of controlling passive centrifugal hydraulic clamping force in a continuously variable ball planetary comprising applying an additive passive centrifugal axial hydraulic clamping force to a first clamping element, at any rotational speed, causing the clamping element to engage an first axial force mechanism in contact with a first drive ring through a cam bearing.
  • the centrifugal hydraulic clamping force applied by the first clamping element is combined with a cam clamp load from the first axial force mechanism to increase pressure between the first drive ring and the rotating traction planets.
  • the continuously variable ball planetary is in overdrive.
  • a method of controlling passive centrifugal hydraulic clamping force in a continuously variable ball planetary comprising applying an additive passive centrifugal axial hydraulic clamping force to a second clamping element, at any rotational speed, causing the clamping element to engage a second axial force mechanism in contact with a second drive ring through a cam bearing.
  • the centrifugal hydraulic clamping force applied by the second clamping element is combined with a cam clamp load from the second axial force mechanism to increase pressure between the second drive ring and the rotating traction planets.
  • a method of controlling passive centrifugal hydraulic clamping force between rotating traction planets and a first drive ring and a second drive ring for a continuously variable ball planetary comprising applying an additive passive centrifugal axial hydraulic clamping force to a first clamping element and a second clamping element, at high rotational speed, causing the first and second clamping elements to engage an first axial force mechanism and a second axial force mechanism in contact with the first drive ring and the second drive ring through cam bearings.
  • the centrifugal hydraulic clamping force applied by the first clamping element and the second clamping element is combined with a cam clamp load from the first axial force mechanism and the second axial force mechanism to increase pressure between the first drive ring, the second drive ring, and the rotating traction planets.
  • the clamping element with the higher revolutions per minute is the active speed-dependent clamping device.
  • a non-active cam driver would react to the active clamp load and the pressure from the fluid within the variator to become the active cam driver.
  • the centrifugal clamping force is controlled by hydraulic pressure applied to a clamping element, whereby said hydraulic pressure generates an additive force in excess of a cam clamp load generated by the first or second axial force mechanism, in the continuously variable ball planetary.
  • the combined clamping force of the clamping element and the axial force mechanism exceeds the design value of the cam clamp load of a ball-and-cam axial force mechanism to produce a useful increase in total clamping force at low torque/high speed.
  • Figure 1 is a side sectional view of a ball-type variator
  • Figure 2 depicts a block diagram of a passive centrifugal clamping mechanism illustrating a cross-section of rotating cavity containing hydraulic fluid and a clamping element.
  • Figure 3 depicts a representative isometric view of a planetary ball variator comprising optional fluid output or bleed ports.
  • Figure 4 depicts a representative cross-section view of a planetary ball variator in Figure 3 with a representative depiction of a rotating cavity for hydraulic fluid and a clamping element.
  • Figure 5 depicts a detail representative section view of Figure 4, showing one half of a CVP.
  • Figure 6 depicts a representative graph of the centrifugal force (N) generated vs. RPM of the planetary ball variator at different radial bleed hole locations, controlling the amount of fluid to push the piston.
  • Figure 7 depicts a representative isometric view of another planetary ball variator with an integrated speed wheel in the cam driver; notched captures between the cam driver and cam ring to transfer torque; and optional fluid output, or bleed ports.
  • Figure 8 depicts a representative cross-section view of a planetary ball variator in Figure 7 with a representative depiction of a rotating cavity for hydraulic fluid and a clamping element.
  • Figure 9 depicts a detail representative cross-section view of Figure 7 showing one half of a CVP.
  • Figure 10 depicts a detail representative cross-section view of Figure 7 illustrating only the main shaft, cam driver, clamping element and cam ring.
  • Figures 11-A, 11-B and 11-C depict side, front ISO and rear ISO cross-section views of Figure 7 illustrating only the cam driver, clamping element and cam ring.
  • Figure 12 depicts a detail section view of the interface of the cam driver, clamping element and cam ring of Figure 7.
  • Figure 13 depicts another detail section view illustrating a lip capture feature of the clamping element utilized to capture and distribute hydraulic fluid to the piston within the variator.
  • a continuously variable ball planetary variator produces a passive centrifugal hydraulic clamping force that exceeds the design value of a cam clamp load of a ball-and-cam mechanism at design speed, reducing or counteracting the hydrodynamic lift between the planetary traction planets, input and output drive rings, and improving output torque and efficiency.
  • FIG. 1 The cross-section of a typical CVP is shown in FIG. 1.
  • a typical CVP comprises a number of balls, or traction planets 997, two discs with a conical surface contact with the traction planets, as input 995 and output 996, and an idler 999.
  • the traction planets are mounted on axes 998, themselves held in a cage or carrier allowing changing of the ratio by tilting the balls' axes.
  • Other types of ball CVTs also exist, like the one produced by Milner, but are slightly different.
  • the CVP itself works with a traction fluid.
  • the lubricant between the ball and the conical rings acts as a solid at high pressure, transferring the power from the input ring, through the balls, to the output ring.
  • the ratio is changed between input and output.
  • the ratio is one, when the axis is tilted the distance between the axis and the contact point change, modifying the overall ratio. All the traction planets' axes are tilted at the same time with a mechanism included in the cage.
  • the terms "input ring”, and “output ring” may alternately be referred to as a first or second “drive ring”.
  • operationally linked refers to a relationship (mechanical, linkage, coupling, etc.) between elements whereby operation of one element results in a corresponding, following, or simultaneous operation or actuation of a second element. It is noted that in using said terms to describe inventive embodiments, specific structures or mechanisms that link or couple the elements are typically described. However, unless otherwise specifically stated, when one of said terms is used, the term indicates that the actual linkage or coupling may take a variety of forms, which in certain instances will be readily apparent to a person of ordinary skill in the relevant technology.
  • radial is used here to indicate a direction or position that is perpendicular relative to a longitudinal axis of a transmission or variator.
  • axial refers to a direction or position along an axis that is parallel to a main or longitudinal axis of a transmission or variator.
  • Traction drives usually involve the transfer of power between two elements by shear forces in a thin fluid layer trapped between the elements.
  • the fluids used in these applications usually exhibit traction coefficients greater than conventional mineral oils.
  • the traction coefficient ( ⁇ ) represents the maximum available traction forces which would be available at the interfaces of the contacting components and is a measure of the maximum available drive torque.
  • friction drives generally relate to transferring power between two elements by frictional forces between the elements.
  • the CVTs described here may operate in both tractive and frictional applications.
  • the CVT operates at times as a friction drive and at other times as a traction drive, depending on the torque and speed conditions present during operation.
  • the continuously variable ball planetary 100 comprising: a plurality of tilting traction planets 997 mounted on a carrier 114, the traction planets in contact with a first drive ring 995 and a second drive ring 996 and traction fluid; at least one axial force mechanism 102 in contact with at least one of the first drive ring or the second drive ring through a cam bearing 107; at least one enclosed rotating cavity 108 optionally comprising bleed holes 104a; at least one clamping element 106 (a piston/ring), adjacent to and at least partially within the rotating cavity 108, in approximate contact with the axial force mechanism 102; and hydraulic fluid within the rotating cavity.
  • the hydraulic fluid is subject to rotational forces during operation of the CVT 100.
  • the clamping element 106 is a ring or a piston.
  • traction fluid means a fluid intended for the purpose of lubrication and or preventing seizure and abrasion between the discs and traction planets by preventing them from coming into direct contact with each other. These fluids flow between the discs and planets, lubricating the surfaces for protection and transmitting power between them. This potential to transmit power is referred to as the traction coefficient.
  • hydroaulic fluid means a fluid used to convey power or generate a force, such as a clamping force.
  • Hydraulic systems like those described herein work most efficiently if the hydraulic fluid used has zero compressibility. In some applications and embodiments, the terms are used
  • the hydraulic pressure applied to the clamping element is combined with a cam clamp load provided by the at least one axial force mechanism 109 to apply axial loading to at least one of the first drive ring 995 or the second drive ring 996 to increase pressure against the tilting traction planets 997.
  • the increased axial force is applied to the first drive ring and/or second drive ring to counteract hydrodynamic lift between the tilting traction planets and the first drive ring and/or second drive ring.
  • the axial force generated by the axial force mechanism 109 is variable with torque and speed. Under certain operating conditions, for example, at high speeds, the axial force generated by the axial force mechanism 109 may be insufficient to transmit the desired torque.
  • An additional axial force may be applied by passive means through the hydraulic centrifugal force applied to the clamping element 2.
  • a clamping element 2 applies a variable hydraulic clamping force to at least one axial force mechanism 102.
  • the variable hydraulic clamping force is produced by centrifugal force generated by the hydraulic fluid in the fluid cavity 3 exerted on the clamping element 2 (piston/ring) resulting from a rotational speed of the clamping element, causing it to move off of the hard stop 1.
  • an optional O-ring 9 exists between the cavity and the clamping element.
  • variable hydraulic clamping force 4 is a squared function of the rotational speed 8 of the clamping element 2.
  • the radial locations of the optional bleed holes 104a in at least one enclosed, rotating cavity 108 determines a gain of the clamping force with respect to the squared speed of the clamping element.
  • the cam bearing is configured for relative rotation with respect to the first drive ring, the relative rotation corresponding to an operating torque of the CVT, and wherein the bleed holes are arranged to be blocked by the cam bearing under high torque operation.
  • the cam bearing uncovers the bleed holes under low torque operation.
  • the clamping force is defined as: dp
  • F D clamping force
  • ⁇ angular velocity in radians/second
  • r 2 maximum radius of the piston face
  • ⁇ inner radius of the piston
  • R 0 inner radius of hydraulic fluid (bleed hole radius / exit radius of fluid
  • p fluid density
  • ⁇ mathematical constant.
  • R 0 ⁇
  • the clamping force may be determined by other formulae comprising similar and /or different variables known to those skilled in the art.
  • the radial locations of the optional bleed holes 104a are within a range of about 0.1 mm and 200.0 mm, 10.0 mm and 175.0 mm, 20.0 mm and 150.0 mm, 30.0 mm and 130.0 mm, 30.0 mm and 120.0 mm, 30.0 mm and 1 10.0 mm, 30.0 mm and 100.0 mm, 30.0 mm and 90.0 mm, 30.0 mm and 80.0 mm, 30.0 mm and 75.0 mm, 30.0 mm and 70.0 mm, 30.0 mm and 65.0 mm, 30.0 mm and 60.0 mm, 30.0 mm and 55.0 mm, 30.0 mm and 50.0 mm, 30.0 mm and 45.0 mm, 30.0 mm and 40.0 mm, 35.0 mm and 80.0 mm, 40.0 mm and 80.0 mm, 45.0 mm and 80.0 mm, 50.0 mm and 80.0 mm, 50.0 mm and 80.0 mm, 60.0 mm,
  • the number of the optional bleed holes 104a is within about 0 and 30.
  • the bleed hole is inside the diameter of the piston.
  • the diameter of the optional bleed holes 104a is within about 0.20 mm and 8.0 mm.
  • the optional bleed holes 104a further comprise plugs 104b.
  • the CVP 100 comprises a cam driver 101, a cam ring 102, a cam bearing race 103, optional bleed holes 104a, bleed hole plugs 104b and a main shaft 105.
  • the cross-sectional view reveals the inner structure of an illustrative CVP 100 comprising the relative placement of hydraulic ports 1 lOa/b, cam bearings 107, the rotary hydraulic cavity 108, an optional O-ring 113 and the preload nut 109, with respect to the other variator components already described.
  • the term “about” or “approximately” means an acceptable error for a particular value as determined by one of ordinary skill in the art, which depends in part on how the value is measured or determined. In certain embodiments, the term “about” or “approximately” means within 1 , 2, 3, or 4 standard deviations. In certain embodiments, the term “about” or “approximately” means within 30%, 2,5%, 20%, 15%, 10%, 9%, 8%, 7%, 6%, 5%, 4%, 3%, 2%, 1%, 0.5%, 0.1%, or 0.05% of a given value or range.
  • the term "about” or “approximately” means within 40.0 mm, 30.0 mm, 20.0 mm, 10.0mm 5.0 mm 1 .0 mm, 0.9 mm, 0.8 mm, 0.7 mm, 0.6 mm, 0.5 mm, 0.4 mm, 0.3 mm, 0.2 mm or 0.1 mm of a given value or range.
  • a method of generating passive centrifugal hydraulic clamping force in a continuously variable ball planetary comprising applying an additive passive centrifugal axial hydraulic clamping force to a first clamping element (piston/ring), at any rotational speed, causing the clamping element 106 to engage a first axial force mechanism 102 in contact with a first drive ring 995 through the cam bearing 107.
  • the centrifugal clamping force applied by the first clamping element 106 is combined with a clamp load from the first axial force mechanism 102 to increase pressure between the first drive ring 995 and the rotating traction planets 997.
  • the centrifugal clamping force applied by the first clamping element 106 is combined with a clamp load from a preload nut 109 to increase pressure between the first drive ring 995 and the rotating traction planets 997.
  • the continuously variable ball planetary 100, 200 is in overdrive.
  • the axial force mechanism is a cam 102.
  • the cam is single-sided, or double-sided.
  • the cam is uni-directional or bi-directional.
  • the axial force mechanism is a single cam (on the input or output ring, 995, 996) or a dual cam (on the input ring and output ring).
  • the axial force mechanism is a roller load cam.
  • the clamping element is an axially sliding element, (e.g.: a stepped ring), in intimate, sealed contact with a rotating cavity having optional bleed holes 104a positioned radially, adjacent the diametral face of the clamping element, and ideally in the approximate radial center of either a first or a second drive ring face, (in a single cam configuration).
  • the clamping element is immediately adjacent, to and in contact with the first or second drive ring through cam bearings.
  • the hydraulic pressure within the cavity created by centrifugal force, acting on the hydraulic fluid in the cavity exerts a force on the adjacent clamping element which exceeds the pre-loaded clamping force, causing the clamping element to slide axially off of a hard stop on the face of the rotating cavity and apply a greater axial force or clamping force to the drive ring of the CVP than would have otherwise been available from the axial force mechanism alone.
  • the clamping elements are axially sliding elements, (e.g.: a stepped ring), in intimate, sealed contact with rotating cavities comprising optional bleed holes positioned radially, adjacent the diametral face of more two clamping elements, and ideally in the approximate radial center of both a first and a second drive ring face, (such as in a dual cam configuration).
  • the clamping elements are immediately adjacent, to and in contact with the first and second drive ring through cam bearings.
  • the hydraulic pressure within the cavities created by centrifugal force, acting on the hydraulic fluid in the cavity exerts a force on the adjacent clamping element which exceeds the pre-loaded clamping force, causing the clamping element to slide axial off of a hard stop on the face of the rotating cavity and apply a greater axial force or clamping force to the input drive ring and output drive ring of the CVP than would have been available from the axial force mechanisms alone, as previously illustrated and described in FIG. 2.
  • the CVP comprises a Cam Driver 201, a Cam Ring 202, a Cam Bearing Race 203, Bleed Holes 204a and Plugs 204b, a Main Shaft 205, a Piston / Ring 206, a Cam Bearing 207, a Rotary Hydraulic Fluid Cavity 208, a Pre-load Nut 209, Hydraulic Fluid Input Ports (external) 210a, Hydraulic Fluid Input Port (internal) 210b, Torque Transfer Notches (integrated into the Cam Driver) 211, an Integrated Speed Wheel 212, O-Rings (optional) 213, a Carrier / Stator 214, a Cam Bearing track 217, a Piston Support Notch 218, a Piston Ring Hydraulic Fluid Capture Lip 219, an Idler Bearing 220, a Cam Driver Mount
  • a method of generating passive centrifugal hydraulic clamping force in a continuously variable ball planetary comprising applying an additive passive centrifugal axial hydraulic clamping force to a second clamping element (piston/ring), at rotational speed, causing the clamping element to engage an second axial force mechanism in contact with a second drive ring through the cam bearings.
  • the centrifugal clamping force applied by the second clamping element is combined with a cam clamp load from the second axial force mechanism to increase pressure between the second drive ring and the rotating traction planets.
  • the centrifugal clamping force applied by the second clamping element is combined with a cam clamp load from the second axial force mechanism to increase pressure between the second drive ring and the rotating traction planets.
  • a method of generating passive centrifugal clamping force between rotating traction planets and a first drive ring and a second drive ring for a continuously variable ball planetary comprising applying an additive passive centrifugal axial hydraulic clamping force to a first clamping element (piston/ring) and a second clamping element (piston/ring), at rotational speed, causing the first and second clamping elements to engage a first axial force mechanism and a second axial force mechanism in contact with the first drive ring and the second drive ring through the cam bearings.
  • the centrifugal clamping force applied by the first clamping element (piston/ring) and the second clamping element (piston/ring) is combined with a system preload from the first axial force mechanism and the second axial force mechanism to increase pressure between the first drive ring, the second drive ring, and the rotating traction planets.
  • a side of the variator with higher revolutions per minute would be an active speed-dependent clamp side.
  • a non-active cam driver would react to the active clamp load and the pressure from the fluid within the variator to become the active cam driver.
  • the non-active cam is for example, ring 2, [assuming the system is in overdrive], and the input [Rl] is at a low torque state, and if the hydraulic clamp mechanism on R2 is producing a higher clamp force due to its speed, then it reacts to become the active clamp device.
  • the input torque is 70 Nm
  • the SR speed ratio
  • the clamp load due to Rl cam ramps would be ⁇ 11,000 N, then the hydraulic clamp force from R2 would be greater than 37,000 N and hence would be the 'active' clamping device. If the device was on Rl, then one should get a minimum -12,000 N, which is still larger than the Rl cam ramps.
  • the centrifugal clamping force is generated by hydraulic pressure applied to a clamping element, whereby said hydraulic pressure generates an additive force in excess of a cam clamp load generated by the first or second axial force mechanism, in the continuously variable ball planetary.
  • the combined clamping force of the clamping element and the axial force mechanism exceeds a predetermined value of the cam clamp load of a ball-and-cam axial force mechanism to produce a useful increase in total clamping force at low torque/high speed.
  • a predetermined value of the cam clamp load of a ball-and-cam axial force mechanism to produce a useful increase in total clamping force at low torque/high speed.
  • a continuously variable planetary transmission comprising a variator with passive centrifugal clamping means, the variator comprising: a plurality of tilting traction planets mounted on a carrier, the traction planets in contact with a first drive ring and a second drive ring; at least one axial force mechanism; at least one enclosed, rotating cavity ; at least one clamping element (piston/ring), adjacent to and at least partially within the rotating cavity, in approximate contact with the axial force mechanism and hydraulic fluid within the rotating cavity, wherein the hydraulic fluid is subject to centrifugal force as a result of rotational speeds of the continuously variable ball planetary; wherein at least one rotating cavity, generates hydraulic pressure at any rotational speeds and exerts a force on at least one clamping element adequate to fully engage at least one axial force mechanism, wherein the force generated on the first and/or second drive ring is greater than a torque controlled ramp force provided by at least one axial force mechanism alone.
  • the rotating cavity comprises bleed holes.
  • a method of controlling passive centrifugal hydraulic clamping force in a continuously variable ball planetary comprising applying an additive passive centrifugal axial hydraulic clamping force to a first clamping element, at any rotational speed, causing the clamping element to engage an first axial force mechanism in contact with a first drive ring through a cam bearing.
  • the centrifugal hydraulic clamping force applied by the first clamping element is combined with a cam clamp load from the first axial force mechanism to increase pressure between the first drive ring and the rotating traction planets.
  • the continuously variable ball planetary is in overdrive.
  • a method of controlling passive centrifugal hydraulic clamping force in a continuously variable ball planetary comprising applying an additive passive centrifugal axial hydraulic clamping force to a second clamping element, at any rotational speed, causing the clamping element to engage a second axial force mechanism in contact with a second drive ring through a cam bearing.
  • the centrifugal hydraulic clamping force applied by the second clamping element is combined with a cam clamp load from the second axial force mechanism to increase pressure between the second drive ring and the rotating traction planets.
  • a method of controlling passive centrifugal hydraulic clamping force between rotating traction planets and a first drive ring and a second drive ring for a continuously variable ball planetary comprising applying an additive passive centrifugal axial hydraulic clamping force to a first clamping element and a second clamping element, at high rotational speed, causing the first and second clamping elements to engage an first axial force mechanism and a second axial force mechanism in contact with the first drive ring and the second drive ring through cam bearings.
  • the centrifugal hydraulic clamping force applied by the first clamping element and the second clamping element is combined with a cam clamp load from the first axial force mechanism and the second axial force mechanism to increase pressure between the first drive ring, the second drive ring, and the rotating traction planets.
  • the clamping element with the higher revolutions per minute is the active speed-dependent clamping device.
  • a non-active cam driver would react to the active clamp load and the pressure from the fluid within the variator to become the active cam driver.
  • the centrifugal clamping force is controlled by hydraulic pressure applied to a clamping element, whereby said hydraulic pressure generates an additive force in excess of a cam clamp load generated by the first or second axial force mechanism, in the continuously variable ball planetary.
  • the combined clamping force of the clamping element and the axial force mechanism exceeds the design value of the cam clamp load of a ball-and-cam axial force mechanism to produce a useful increase in total clamping force at low torque/high speed.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

Selon la présente invention, un variateur planétaire à bille à variation continue produit une force de serrage hydraulique centrifuge passive qui dépasse la valeur de conception d'une charge de serrage de came d'un mécanisme à bille et came à la vitesse nominale, ce qui réduit ou contre la portance hydrodynamique entre les engrenages planétaires, les bagues d'entraînement d'entrée et de sortie, et ce qui améliore le couple et le rendement de sortie.
PCT/US2016/027496 2015-04-17 2016-04-14 Serrage hydraulique centrifuge passif pour fonctionnement planétaire à variation continue à grande vitesse WO2016168439A1 (fr)

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US9933054B2 (en) 2013-03-14 2018-04-03 Dana Limited Continuously variable transmission and an infinitely variable transmission variator drive
US10006529B2 (en) 2014-06-17 2018-06-26 Dana Limited Off-highway continuously variable planetary-based multimode transmission including infinite variable transmission and direct continuously variable transmission
US10088026B2 (en) 2012-09-07 2018-10-02 Dana Limited Ball type CVT with output coupled powerpaths
WO2018222660A1 (fr) * 2017-05-31 2018-12-06 Dana Limited Composants et ensembles pour transmission planétaire à variation continue de type à billes
EP3524852A1 (fr) * 2018-02-08 2019-08-14 Motive Power Industry Co., Ltd. Mécanisme de transfert de puissance bidirectionnelle pour transmission variable continue
EP3530982A1 (fr) * 2018-02-23 2019-08-28 Motive Power Industry Co., Ltd. Mécanisme de transfert de puissance équipé d'une rampe bidirectionnelle et conçu pour être utilisé avec transmission variable en continu
US11219905B2 (en) * 2015-09-17 2022-01-11 Gea Mechanical Equipment Gmbh Cooling device for a drive of a solid bowl screw centrifuge

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* Cited by examiner, † Cited by third party
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US10088026B2 (en) 2012-09-07 2018-10-02 Dana Limited Ball type CVT with output coupled powerpaths
US9933054B2 (en) 2013-03-14 2018-04-03 Dana Limited Continuously variable transmission and an infinitely variable transmission variator drive
US10006529B2 (en) 2014-06-17 2018-06-26 Dana Limited Off-highway continuously variable planetary-based multimode transmission including infinite variable transmission and direct continuously variable transmission
US11219905B2 (en) * 2015-09-17 2022-01-11 Gea Mechanical Equipment Gmbh Cooling device for a drive of a solid bowl screw centrifuge
WO2018222660A1 (fr) * 2017-05-31 2018-12-06 Dana Limited Composants et ensembles pour transmission planétaire à variation continue de type à billes
EP3524852A1 (fr) * 2018-02-08 2019-08-14 Motive Power Industry Co., Ltd. Mécanisme de transfert de puissance bidirectionnelle pour transmission variable continue
EP3530982A1 (fr) * 2018-02-23 2019-08-28 Motive Power Industry Co., Ltd. Mécanisme de transfert de puissance équipé d'une rampe bidirectionnelle et conçu pour être utilisé avec transmission variable en continu
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