JP2017537285A - Three-mode planetary mechanism continuously variable transmission for front wheel drive and rear wheel drive - Google Patents

Three-mode planetary mechanism continuously variable transmission for front wheel drive and rear wheel drive Download PDF

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JP2017537285A
JP2017537285A JP2017530122A JP2017530122A JP2017537285A JP 2017537285 A JP2017537285 A JP 2017537285A JP 2017530122 A JP2017530122 A JP 2017530122A JP 2017530122 A JP2017530122 A JP 2017530122A JP 2017537285 A JP2017537285 A JP 2017537285A
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Japan
Prior art keywords
carrier
continuously variable
ring
gear
clutch
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Pending
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JP2017530122A
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Japanese (ja)
Inventor
エス. ヴァンセラス、ジョゼフ
エス. ヴァンセラス、ジョゼフ
イー. メファム、シャウン
イー. メファム、シャウン
エル. パリス、チェスター
エル. パリス、チェスター
マッキンドー、ゴードン
ジェイ. ハカ、レイモンド
ジェイ. ハカ、レイモンド
ダブリュ. フィリップス、アンドリュー
ダブリュ. フィリップス、アンドリュー
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ダナ リミテッド
ダナ リミテッド
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Priority to US201462089126P priority Critical
Priority to US62/089,126 priority
Priority to US201562144751P priority
Priority to US62/144,751 priority
Application filed by ダナ リミテッド, ダナ リミテッド filed Critical ダナ リミテッド
Priority to PCT/US2015/064087 priority patent/WO2016094254A1/en
Publication of JP2017537285A publication Critical patent/JP2017537285A/en
Application status is Pending legal-status Critical

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H37/00Combinations of mechanical gearings, not hereinbefore provided for
    • F16H37/02Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings
    • F16H37/06Combinations of mechanical gearings, not hereinbefore provided for 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
    • F16H37/08Combinations of mechanical gearings, not hereinbefore provided for 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
    • F16H37/0833Combinations of mechanical gearings, not hereinbefore provided for 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
    • F16H37/084Combinations of mechanical gearings, not hereinbefore provided for 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
    • F16H37/0853CVT using friction between rotary members having a first member of uniform effective diameter cooperating with different parts of a second member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H15/00Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04Gearings providing a continuous range of gear ratios
    • F16H15/06Gearings 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
    • F16H15/26Gearings 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
    • F16H15/28Gearings 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H15/00Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/48Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
    • F16H15/50Gearings providing a continuous range of gear ratios
    • F16H15/52Gearings providing a continuous range of gear ratios in which a member of uniform effective diameter mounted on a shaft may co-operate with different parts of another member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H37/00Combinations of mechanical gearings, not hereinbefore provided for
    • F16H37/02Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings
    • F16H37/06Combinations of mechanical gearings, not hereinbefore provided for 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
    • F16H37/08Combinations of mechanical gearings, not hereinbefore provided for 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
    • F16H37/0833Combinations of mechanical gearings, not hereinbefore provided for 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
    • F16H37/084Combinations of mechanical gearings, not hereinbefore provided for 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
    • F16H2037/088Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
    • F16H2037/0886Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges

Abstract

A continuously variable transmission for front wheel drive or rear wheel drive includes an input shaft, an output shaft, a continuously variable tilting ball planetary variator, and a composite planetary array having first, second, third, and fourth rotating elements. And a plurality of torque transmission devices. The compound planetary arrangement has a simple single pinion gear set and a compound double pinion gear set that have a fixedly connected planet carrier and a fixedly connected ring gear, and create a joint planetary gear carrier and a joint ring gear. The outer planetary gear engages a ring gear that drives the output shaft. The selective torque transmission device includes a clutch and brakes the clutch. Alternative variations in the configuration of the continuously variable transmission use a variation in the configuration of the torque transmission device, or use two simple planetary gear set assemblies instead of the unused complex planetary array.

Description

CROSS REFERENCE TO RELATED APPLICATIONS This application claims the benefit of US Provisional Application No. 62 / 089,126, filed Dec. 8, 2014, and is filed on April 8, 2015. The benefit of 62 / 144,751 is also claimed and these applications are incorporated herein by reference.

  A vehicle with a drive system that includes a continuously variable transmission allows the vehicle driver or vehicle control system to change the drive ratio in a continuously variable manner, and the vehicle power source operates at the most efficient rotational speed. Make it possible to do. Transmissions are becoming more complex because the speed of the engine must be more closely controlled to limit the consumption and release of car fuel. Furthermore, the speed and efficiency of the transmission components are equally important.

  A continuously variable transmission has been proposed that provides a vehicle with a continuously variable transmission that has a design that avoids high pinion and / or carrier speeds and other drawbacks in existing three-mode power flows.

  A fixed housing (ground), an input shaft, a variator having a first ring assembly and a second ring assembly, a first sun gear, a first sun gear, and a drive mechanism connected to the first ring gear A first planetary gear set having a first set of planetary gears to be combined, and a first carrier; a second sun gear; a second sun gear coupled to the second ring gear; A second set of planetary gears to be combined, and a second planetary gear set including a second carrier, a first selectable torque transmission device, a second selectable torque transmission device, and a third selectable A torque transmission device and an output shaft, wherein the input shaft is fixedly connected to the first ring assembly, and the second ring assembly is fixedly connected to the first sun gear and the second sun gear. The second carrier is drivingly engaged with the first carrier, the output shaft is drivingly connected to the first ring gear and the second ring gear, and the first selectable torque transmission device is the first carrier. And connecting the second carrier to the ground to establish a first forward variable range of the overall transmission speed ratio, the second selectable torque transmission device connecting the first carrier to the input shaft, The second forward-side variable range of the overall transmission speed ratio is established, and the third selectable torque transmission device connects the first carrier and the second carrier to the ground so that the overall transmission speed ratio can be varied backward. Establishing a range, the variator controls a variable speed ratio between the speed of the first ring assembly and the speed of the second ring assembly, thereby adjusting the overall transmission speed ratio in any of the variable ranges; Stepless Speed machine are provided herein. In some embodiments, the first selectable torque transmission device, the second selectable torque transmission device, and the third selectable torque transmission device include a first brake, a clutch, and a second brake. including.

  A fixed housing (ground), an input shaft, a variator having a first ring assembly and a second ring assembly, a first sun gear, a first sun gear, and a drive mechanism connected to the first ring gear A first planetary gear set having a first set of planetary gears to be combined, and a first carrier; a second sun gear; a second sun gear coupled to the second ring gear; A second planetary gear set having a second set of planetary gears combined and a second carrier; an output shaft; a first selectable torque transmission coupled to the second sun gear and a stationary housing. Apparatus, a second selectable torque transmission device coupled to the first carrier and the input shaft, and a third selectable torque transmission device coupled to the second carrier and the stationary housing. The input shaft is fixedly connected to the first ring assembly, the second ring assembly is fixedly connected to the second ring gear and the first sun gear, and the first carrier is the second carrier The output shaft is drivingly connected to the first ring gear, and the engagement of the first selectable torque transmission device corresponds to the first forward variable range of the overall transmission speed ratio, The engagement of the second selectable torque transmission device corresponds to the second forward variable range of the overall transmission speed ratio, and the engagement of the third selectable torque transmission device corresponds to the reverse variable range of the overall transmission speed ratio. The variator controls the variable speed ratio between the speed of the first ring assembly and the speed of the second ring assembly, thereby adjusting the overall transmission speed ratio in any of the variable ranges. A step transmission is described herein. It is provided Oite. In some embodiments, the first selectable torque transmission device, the second selectable torque transmission device, and the third selectable torque transmission device include a first brake, a clutch, and a second brake. including.

  A fixed housing (ground), an input shaft, a variator having a first ring assembly and a second ring assembly, a first sun gear, a first sun gear, and a drive mechanism connected to the first ring gear A first planetary gear set having a first set of planetary gears to be combined, and a first carrier; a second sun gear; a second sun gear coupled to the second ring gear; A first planetary gear set having a second set of planetary gears combined and a second carrier, an output shaft, a first ring gear and a first selectable torque transmission device coupled to the ground And a second selectable torque transmission device coupled to the first carrier and the input shaft, and a third selectable torque transmission device coupled to the first carrier and the ground, The force shaft is fixedly connected to the first ring assembly of the variator, the second ring assembly is fixedly connected to the first ring gear and the second sun gear, and the first sun gear is connected to the second ring The output shaft is drivingly connected to the second carrier, the engagement of the first selectable torque transmission device corresponds to the first forward variable range of the overall transmission speed ratio, The engagement of the second selectable torque transmission device corresponds to the second forward variable range of the overall transmission speed ratio, and the engagement of the third selectable torque transmission device corresponds to the reverse variable range of the overall transmission speed ratio. The variator controls the variable speed ratio between the speed of the first ring assembly and the speed of the second ring assembly, thereby adjusting the overall transmission speed ratio in any of the variable ranges. The stage transmission is this specification It is provided in. In some embodiments, the three selectable torque transmission devices include a first brake, a clutch, and a second brake.

  In any one or more of the transmissions provided herein, the variator is a ball-type variator, and the variator rotatably supports a plurality of swiveling axles that are rotatably disposed around a power transmission shaft. And a swiveling axle that each further rotatably supports a ball, wherein the first ring assembly and the second ring assembly each have a ball contact area in continuous contact with each of the balls. And the carrier assembly moves in a controlled manner within a narrow range of angles to cause the swiveling axle to change orientation, thereby changing the variable speed ratio between the first ring assembly and the second ring assembly. .

  In any one or more of the transmissions provided herein, as the variator speed ratio increases, the overall transmission speed ratio in the first forward range increases and the overall transmission in the second forward range. The speed ratio decreases and the overall transmission speed ratio within the reverse range becomes more negative. In some embodiments, if the speed ratio of the variator is near the upper limit of the variable speed ratio range, but still within that range, the overall transmission speed ratio in the first forward range and the second forward range is The second selectable torque transmission device may be engaged synchronously while in the first forward range, while the first selectable torque transmission device is in the second forward range. A fixed ratio transmission mode of operation that can be engaged synchronously and does not transmit power through the variator is established by using the first selectable torque transmission device and the second selectable torque transmission device simultaneously. .

  In any one or more of the transmissions provided herein, the transmission may be utilized in both front wheel drive vehicles and rear wheel drive vehicles.

  As used herein, in any one or more of the transmissions provided, the transmission can selectively connect any two of the rotating elements of the first planetary gear set or the second planetary gear set. This further includes an optional fourth clutch that rotates all of the elements simultaneously and establishes a third forward range. In some embodiments, when the fourth clutch is engaged, the entire gear set rotates as a single unit, causing the transmission output speed to be equal to the output speed of the variator, and the overall transmission speed ratio. In the theoretical CVP range, all of the input power is transmitted to the output ring gear via the variator.

  A stationary housing, an input shaft, a variator having a first ring assembly and a second ring assembly, a first sun gear, coupled to the first sun gear, and drivingly engaged with the first ring gear. A first planetary gear set having a first set of planetary gears and a first carrier, and coupled to the second sun gear, the second sun gear, and drivingly engaged with the second ring gear. A second planetary gear set having a second set of planetary gears and a second carrier; and an output shaft, the input shaft being fixedly connected to the first ring assembly, the second ring assembly being , Fixedly connected to the first sun gear and the second sun gear, the second carrier is drivingly engaged with the first ring gear, and the output shaft is drivingly connected to the first ring gear, A continuously variable transmission is provided herein that controls a variable speed ratio between the speed of the first ring assembly and the speed of the second ring assembly, thereby adjusting the overall transmission speed ratio. The

  A variator having an input shaft operably coupled to a rotational power source, a first traction ring assembly and a second traction ring assembly that contact a plurality of balls, each ball having a tiltable rotation axis A first planetary gear set having an assembly; a first sun gear; a first carrier; and a first ring gear; and a second sun gear, a second carrier, and a second ring gear. A second planetary gear set having an interface shift sleeve assembly having a first interface clutch and a second interface clutch, wherein the first traction ring assembly is coupled to the input shaft, and the second traction ring assembly Is coupled to the first sun gear and the second sun gear, The interface clutch selectively connects the first ring gear to the second carrier, and the second interface clutch selectively connects the second ring gear to the first carrier. Provided herein. In some embodiments, the first interface clutch and the second interface clutch include a dog clutch. In some embodiments, the continuously variable transmission further comprises a first selectable clutch coupled to the first ring gear, wherein the first selectable clutch places the first ring gear in the non-rotating housing. Link selectably. In some embodiments, the continuously variable transmission further comprises a second selectable clutch coupled to the input shaft, the second selectable clutch selectively couples the input shaft to the second carrier. . In some embodiments, the power output is transmitted via the second ring gear. In some embodiments, the first selectable clutch or the second selectable clutch includes a friction clutch. In some embodiments, the interface shift sleeve assembly is radially disposed outside the first planetary gear set and the second planetary gear set. In some embodiments, the interface shift sleeve assembly includes a plurality of internal teeth configured to selectively engage the mating surface with the first ring gear and the second ring gear. In some embodiments, the interface shift sleeve assembly includes a plurality of internal teeth configured to selectively engage a mating surface with a first carrier and a second carrier. In some embodiments, the engagement of the interface shift sleeve assembly with the first ring gear corresponds to the engagement of the interface shift sleeve assembly with the second carrier. In some embodiments, the engagement of the interface shift sleeve assembly with the second ring gear corresponds to the engagement of the interface shift sleeve assembly with the first carrier. In some embodiments, the transmission further comprises an output shaft. In some embodiments, the transmission further comprises a second rotatable shaft coupled to the output shaft and the second ring gear. In some embodiments, the output shaft is operably coupled to the differential. In some embodiments, the transmission further comprises a power input interface. In some embodiments, the power input interface includes a torque converter.

  A variator having an input shaft operably coupled to a rotational power source, a first traction ring assembly and a second traction ring assembly that contact a plurality of balls, each ball having a tiltable rotation axis A first planetary gear set having an assembly; a first sun gear; a first carrier; and a first ring gear; and a second sun gear, a second carrier, and a second ring gear. A second planetary gear set having an interface shift sleeve assembly having a first interface clutch and a second interface clutch, wherein the first traction ring assembly is coupled to the input shaft, and the second traction ring is Coupled to the first sun gear, the second traction ring assembly is It is coupled to the second sun gear and interfaces shift sleeve assembly, the continuously variable transmission is provided herein. In some embodiments, the first interface clutch selectably couples the first ring gear to the second carrier. In some embodiments, the second interface clutch selectably couples the second ring gear to the first carrier. In some embodiments, the first interface clutch and the second interface clutch include a dog clutch.

  In any one or more of the transmissions provided herein, the transmission further comprises a direct connection to a rotational power source. In some embodiments, the transmission further comprises an interface shift sleeve assembly having a first interface clutch and a second interface clutch, wherein one or both of the first interface clutch and the second interface clutch is a dog Has a clutch.

  In any one or more of the transmissions provided herein, the variator has traction fluid.

  A vehicle drive system comprising: a power source; one of the continuously variable transmissions described in the present specification that is drivingly engaged with the power source; and a vehicle output unit that is drivingly engaged with the continuously variable transmission. Provided herein. In some embodiments, the power source is drivingly engaged with the vehicle output.

  Provided herein is a vehicle comprising any of the continuously variable transmissions described herein.

  Provided herein is a method comprising providing any of the continuously variable transmissions described herein.

  Provided herein is a method comprising providing a vehicle drive train having any of the continuously variable transmissions described herein.

  Provided herein is a method comprising providing a vehicle having any of the continuously variable transmissions described herein. [Incorporation by reference]

  All publications, patents, and patent applications mentioned in this specification are to the same extent as if each individual publication, patent, or patent application was specifically and individually indicated to be incorporated by reference. , Incorporated herein by reference.

  The novel features of the invention are set forth with particularity in the appended claims. A better understanding of the features and advantages of the present invention will be obtained by reference to the following detailed description that sets forth illustrative embodiments, in which the principles of the invention are utilized, and the accompanying drawings of which:

FIG. 3 is a stick diagram of an embodiment with rear wheel drive of a three-mode transmission described herein.

FIG. 3 is a stick diagram of an embodiment with front wheel drive of a three-mode transmission described herein.

FIG. 3 is a lever diagram of an embodiment of a three-mode transmission described herein.

FIG. 5 is a lever diagram of another embodiment of a three-mode transmission showing an optional synchronous clutch described herein.

It is an alternative block diagram of the compound gear set of a three-mode transmission.

FIG. 6 is another alternative configuration diagram of a composite gear set of a three-mode transmission.

It is side surface sectional drawing of one Embodiment of a ball | bowl type variator.

It is side surface sectional drawing of another embodiment of a ball-type variator.

FIG. 7B is a plan view of a carrier member that can be used in the variator of FIG. 7B.

FIG. 7B is an enlarged side cross-sectional view of the ball of the variator in FIG. 7A having a symmetrical arrangement of the first ring assembly and the second ring assembly.

FIG. 4 is a different block diagram of an embodiment of a three-mode transmission described herein.

FIG. 10 is a lever diagram of the embodiment of the three-mode transmission described in FIG. 9.

FIG. 10 is a stick diagram of the embodiment of the three-mode transmission illustrated in FIG.

FIG. 4 is a different block diagram of an embodiment of a three-mode transmission described herein.

FIG. 13 is a lever diagram of the embodiment of the three-mode transmission described in FIG. 12.

FIG. 13 is a stick diagram of an embodiment of a three-mode transmission described in FIG.

FIG. 4 is a different block diagram of an embodiment of a three-mode transmission described herein.

FIG. 16 is a lever diagram of the embodiment of the three-mode transmission illustrated in FIG. 15.

FIG. 16 is a stick diagram of an embodiment of a three-mode transmission described in FIG.

FIG. 3 is a stick diagram of an embodiment of a three-mode transmission using a sliding coupling and a double dog clutch for a rear wheel drive configuration described herein.

FIG. 3 is a stick diagram of an embodiment of a three-mode transmission having axially arranged sliding linkages for the front wheel drive configuration described herein.

  The speed ratio of a continuously variable transmission may have the advantage of providing a smoother and continuous transition from a low speed ratio to a high speed ratio. However, conventional continuously variable transmissions can be more complex than ideal.

  In recent years, continuously variable transmissions have been proposed that provide vehicles with a continuously variable transmission gear having a design that avoids high pinion and / or carrier speeds and other drawbacks in existing three-mode power flows.

  Continuously variable transmissions or CVTs include, in non-limiting examples, many types such as belt types with variable pulleys, toroidal types, and conical types. The principle of CVT is to enable the engine to operate at the most efficient rotational speed by changing the transmission ratio in a stepless manner according to the vehicle speed and the driver's torque demand (throttle position). It is. If necessary, the CVT is also configured to shift to the most optimal ratio that provides more power, for example when accelerating. The CVT is configured to change the ratio from the minimum ratio to the maximum ratio without any interruption of power transmission, unlike a normal transmission that requires an interruption of the transmitted power.

  Provided herein is a CVT configuration based on a CVP, or ball-type variator, also known as a continuously variable planetary. The basic concept of a ball-type continuously variable transmission is described in US 20060084549 and AU2011224083A1, and US Pat. Nos. 8,469,856 and 8,870,711, which are incorporated herein by reference in their entirety. It is. Such a CVT adapted as described throughout this specification has several balls (planets, spheres) 997, an input traction ring 995 and an output traction ring 996 depending on the application, as shown in FIG. 7A. As well as two ring (disk) assemblies with conical contact with the ball, as well as an idler (sun) assembly 999. The ball is attached to the shaft 998 and the burl itself is held in the carrier (stator, cage) assembly, allowing the ratio between the input and output rings to be changed by tilting the ball shaft. . In some embodiments, such a CVT adapted as described throughout the present specification may have several balls (planets, spheres) 1, input traction depending on the application, as shown in FIG. 7B. The ring 2 and the output traction ring 3 include two ring (disk) assemblies having conical contact points with the ball, and an idler (sun) assembly 4. The ball is mounted on a tiltable axle 5 and the ball itself is held in a carrier (stator, cage) assembly having a first carrier member 6 operably connected to a second carrier member 7. The first carrier member 6 can rotate relative to the second carrier member 7, and vice versa. In some embodiments, the first carrier member 6 is optionally substantially fixed in rotation, while the second carrier member 7 is configured to rotate relative to the first carrier member. The reverse is also true. In one embodiment, the first carrier member 6 is provided with a number of radial guide slots 8. As shown in FIG. 7C, the second carrier member 7 is optionally provided with a number of radially offset guide slots 9. The radial guide slot 8 and the radially offset guide slot 9 are adapted to guide the tiltable axle 5. The axle 5 is optionally adjusted to achieve a desired ratio of input speed to output speed during CVT operation. In some embodiments, adjusting the axle 5 involves controlling the position of the first and second carrier members to provide the inclination of the axle 5, thereby adjusting the speed ratio of the variator. There are other types of ball CVTs, such as those disclosed by Milner, but slightly different.

  The operating principle of such a CVP in FIG. 7A is shown in FIG. The CVP itself functions with traction fluid. The traction fluid between the ball and the conical ring functions as a solid at high pressure and transmits power from the input ring to the output ring via the ball. By tilting the ball axis, this ratio can be changed between input and output. If the axis is horizontal, the ratio is 1, and when the axis is tilted, the distance between the axis and the contact changes, changing the overall ratio. All ball axes are tilted simultaneously with the mechanism contained within the carrier and / or idler. Embodiments of the present invention disclosed herein comprise generally spherical planets, each having a tiltable axis of rotation that is optionally adjusted to achieve a desired ratio of input speed to output speed during operation. It relates to the control of the variator and / or CVT used. In some embodiments, the adjustment of the rotational axis may be performed by offsetting the planetary axis angle in the first plane to achieve angular adjustment of the planetary axis in a second plane that is substantially perpendicular to the first plane. Accordingly, the speed ratio of the variator is adjusted accordingly. The angular misalignment in the first plane is referred to herein as “skew”, “skew angle”, and / or “skew state”. The speed ratio of the variator is adjusted by the inclination of the planetary axis.

  As used herein, the terms “ring”, “ring assembly”, “rotating element of a variator assembly”, “traction ring”, or “traction ring assembly” are to be construed as equivalent by those skilled in the art.

  As used herein, the terms “ball”, “traction ball”, “sphere”, “planet”, or “traction planet” are construed as the same by those skilled in the art.

  For illustrative purposes, the term “radial” is used herein to indicate a direction or position that is orthogonal to the longitudinal axis of the transmission or variator. The term “axis” as used herein refers to a direction or position along an axis parallel to the main axis or longitudinal axis of the transmission or variator. For the sake of brevity, similar components with similar reference numbers (eg, bearing 1011A and bearing 1011B) are sometimes collectively referred to by a single reference (eg, bearing 1011). .

  As used herein, “operably connected”, “operably coupled”, “operably coupled”, “operably connected”, “operably coupled” , "Operably coupled", and similar terms are used to describe the relationship between elements by the action of one element resulting in a corresponding, subsequent or simultaneous action or actuation of the second element. (Mechanical, coupling, connection, etc.). When these terms are used to describe embodiments of the invention, it is noted that the specific structures or mechanisms that connect or couple these elements are usually described. However, unless specifically stated otherwise, when one of these terms is used, the term indicates that the actual bond or linkage may take a variety of forms, which in a particular example are those skilled in the art. Will be readily apparent.

  When referring to “traction” herein, it should be noted that the main mode or occupation mode of power transmission does not exclude applications due to “friction”. Here, these are generally understood as different types of power transmission without attempting to make a classification difference between traction and friction drive. Usually, traction drive involves the transmission of power between the elements due to shear forces in a thin fluid layer confined between the two elements. Typically, fluids used in these applications exhibit a traction coefficient that is greater than conventional mineral oil. The traction coefficient (μ) represents the maximum available traction force available at the contacting component interface and is the ratio of the maximum available drive force per contact force. Typically, friction drive generally relates to the transmission of power between the two elements due to the frictional force between the two elements. For the purposes of this disclosure, it should be understood that the CVT described herein can operate in both traction and friction applications. For example, in embodiments where the CVT is used for bicycle applications, depending on the torque and speed conditions present during operation, the CVT may operate as a friction drive in some cases and as a traction drive in other cases. Can do.

  For illustrative purposes, a schematic diagram called a lever diagram may be used herein. A lever diagram, also known as a lever analogy diagram, is a representation of a translation system in the rotating part of a planetary gear system. In certain embodiments, the lever diagram is provided as a visual aid when describing the function of the transmission. In a lever diagram, a compound planetary gear set is often represented by a single vertical line ("lever"). The input torque, output torque, and reaction torque are expressed as a horizontal force with respect to the lever. The movement of the lever relative to the reaction point represents the direction of the rotational speed.

  Configured to avoid high speed and other drawbacks of existing three-mode power flow pinions or carriers while optimizing the speed ratio to provide good and adjustable overall ratio (OAR) and mode overlap A continuously variable transmission for front wheel drive or rear wheel drive is provided herein.

  As shown in the lever diagram of FIG. 3, a fixed housing (ground), an input shaft 70, an output shaft 80, a first rotating element 61, a second rotating element 63, a third rotating element 66, and A gear set having a fourth rotating element 62, a variator assembly 30 having a first rotating element and a second rotating element, a first selectable torque transmission device ("first clutch") 21, a second , Selectable torque transmission device (“second clutch”) 22 and third selectable torque transmission device (“third clutch”) 23, and input shaft 70 includes a first of variator assembly 30. The second rotating element of the variator assembly 30 is fixedly connected to the first rotating element 61 of the gear set and the output shaft 80 is connected to the third rotation of the gear set. The first clutch 21 is fixedly connected to the element 66, and the first rotating element 62 of the gear set is connected to the ground to establish the first forward variable range of the overall transmission speed ratio. Connects the input shaft 70 to the second rotating element 63 of the gear set to establish a second forward variable range of the overall transmission speed ratio, and the third clutch 23 is connected to the second rotating element of the gear set. 63 is connected to ground to establish a reverse variable range of the overall transmission speed ratio, and the variator establishes a control variable ratio between the speed of the first rotating element and the speed of the second rotating element, and A continuously variable transmission 10 for front wheel drive (or rear wheel drive) is provided herein that adjusts the overall transmission speed ratio in any of the variable ranges.

  In some embodiments, such as those described in FIGS. 1 and 2, the gear set includes a first ring gear 41, a first sun gear 42, and a first carrier assembly 43. A simple ("single pinion") planetary gear set 40 and a second (compound or "double pinion" having rotating elements including a second ring gear 51, a second sun gear 52, and a second carrier assembly 53 ”) A complex planetary arrangement comprising a simple planetary gear set having a rotating element with a planetary gear set 50 and a compound planetary gear set, and the first carrier assembly 43 of the first planetary gear set 40 comprises: Of a pinion 44 engaging a first ring gear 41 of a single pinion planetary gear set and a first sun gear 42 of a single pinion planetary gear set. One single set is rotatably supported, and the second carrier assembly 53 of the double pinion planetary gear set 50 engages the second sun gear 52 of the double pinion planetary gear set 50. And a third set of pinions 55 engaging the second set 54 of pinions and the second ring gear 51 of the double pinion planetary gear set, and the first set of first planetary gear sets 40 The first carrier assembly 43 and the second carrier assembly 53 of the second planetary gear set 50 are fixedly connected to form a fixed connection carrier assembly 45, and the first ring gear 41 of the first planetary gear set 40. And the second ring gear 51 of the second planetary gear set 50 is fixedly connected to form a fixed connection ring gear 46, One rotating element is the first sun gear 42, the second rotating element of the gear set is the fixed connection carrier assembly 45, and the third rotating element of the gear set is the fixed connection ring gear 46. The fourth rotating element of the gear set is the second sun gear 52.

  In some embodiments shown in FIGS. 2 and 6, the gear set includes a ring gear 66, an outer set of long pinion gears 64 that mesh with the ring gear 66, and a short pinion gear that meshes with the outer set of the long pinion gear 64. A carrier assembly 63 that rotatably supports the inner set of 65, a first sun gear 61 that meshes with the outer set of the long pinion gear 64, and a second sun gear 62 that meshes with the inner set of the short pinion gear 65. A compound (Ravigneaux) planetary gear set 60, the first rotating element of the gear set is the first sun gear 61, the second rotating element of the gear set is the carrier assembly 63, and the gear set first The third rotating element is a ring gear 66 and the fourth rotating element of the gear set is the second sun Is A 62. In some embodiments, the gear set 60 is a Ravigneaux planetary gear set.

  As shown in FIGS. 7A-7C, a variator is a system that uses a set of rotating tilt balls in a carrier positioned between an input ring and an output ring. When the ball is tilted, its contact diameter changes and the speed ratio changes. Contacting the rotating sphere at two different positions relative to the axis of rotation of the sphere provides a “gear ratio” that can vary from underdrive to overdrive depending on the position of the contacts for input and output torque and speed. As a result, the variator system provides a continuous transition to any ratio within that range. The gear ratio changes by continuously tilting the sphere axis, providing different contact radii, which drive the input and output rings or discs.

  As described above, the variator has a plurality of balls that transmit torque through a plurality of fluid patches. The balls are arranged in a circular arrangement around a central idler (sun) and contact separate input and output traction rings at engagement points around the ball. This configuration allows the input and output to be concentric and compact. As a result, transmission can be smoothly swept through the entire range of ratios while moving, loaded, or stopped.

  The variator itself functions with traction fluid. Traction fluid is placed in the variator for lubrication and traction. When this fluid is subjected to a high contact pressure when in rolling contact between two very hard elements, the ball and the ring, the fluid undergoes an almost instantaneous phase transition to an elastic solid. This is also known as elastohydrodynamic lubrication (EHL). Within this patch of traction, fluid molecules stack and bind to form a solid. As a result, a shearing force and thus a torque can be transmitted. Note that when the element rotates, the rolling element is not actually in physical contact.

  The traction fluid between the ball and the conical ring functions as a solid at high pressure and from the first ring assembly 32 (variator input) through the variator ball 35 to the second ring assembly 33 (variator output). ). By tilting the variator ball shaft 34, the ratio is changed between input and output, as shown in FIG. If each axis of the variator ball is horizontal, the ratio is 1, and when the axis is tilted, the distance between the axis and the contact changes, changing the overall ratio between underdrive and overdrive To do. All variator ball axles are simultaneously tilted at the same angle using a mechanism included in the cage.

  The embodiments of the invention described herein will find many applications. For example, reference is made to vehicle applications, but the continuously variable transmissions described herein can be used in many applications such as, for example, bicycles, automobiles, wind turbines, and power equipment. Embodiments of the present invention described herein include a front-wheel drive or rear-wheel drive transmission for both on-highway vehicles and off-highway vehicles. You will find use.

  In some embodiments of the CVP transmission 10, as already described and now shown in FIGS. 1 and 2, the variator is disposed rotatably about the power transmission shaft, each of which further includes a ball A ball type variator 30 comprising a carrier assembly 31 that rotatably supports a plurality of pivot axles 34 that also rotatably supports 35, wherein the first ring assembly 32 and the second ring assembly 33 are each a ball A ball contact area in continuous contact with all 35. In some embodiments, the first rotating element of the variator 30 is a first ring assembly 32, the second rotating element of the variator 30 is a second ring assembly 32, and the carrier assembly 31 is As previously shown in FIG. 8 in connection with the variator housing, it moves in a controlled manner within a narrow range of angles to cause the swivel axle 34 to change orientation, thereby providing a first ring assembly 32 and a second ring assembly. Change the speed ratio to 33.

  With reference to FIGS. 1 and 2, in one embodiment, the first and second rotating elements of the variator assembly 30 are a first traction ring 32 and a second traction ring 33. In some embodiments, the first and second rotating elements of variator assembly 30 are first traction ring 32 and carrier assembly 34.

  In some embodiments of the transmission, as the speed ratio of the variator between the first ring assembly 32 and the second ring assembly 33 increases, the overall transmission speed ratio within the first forward range increases. The overall transmission speed ratio in the second forward range decreases, and the overall transmission speed ratio in the reverse range becomes more negative. In some embodiments, a transmission having a variator speed ratio that is near the upper limit of the variator speed ratio range but is still within the overall transmission speed ratio range may have the same first forward range and second forward range. And the second clutch can be engaged synchronously while in the first forward range, and the first clutch can be synchronized while in the second forward range. A further fixed ratio transmission mode of operation that can be engaged and does not transmit power through the variator is established by using the first clutch and the second clutch simultaneously. The fixed ratio mode of operation is further described as the intersection of the first and second modes, and theoretically the variator must transmit power when both the first and second clutches are locked. There is no.

  In some embodiments, as shown in FIGS. 2 and 4, the transmission selectively connects any two of the four rotating elements of the planetary gear set 60, thereby allowing all of the elements to be May be further provided with an optional fourth clutch 24 that simultaneously rotates and establishes a third forward range. When engaged, the planetary gear set 60 rotates as a single unit, thereby causing the transmission output speed to be equal to the output speed of the variator, increasing the overall transmission speed ratio, in the example 0. In the theoretical CVP range of 5 to 1.8, all of the input power is transmitted to the ring gear 66 through the variator.

  Alternatively, the continuously variable transmission configuration described herein uses two simple planetary gear set assemblies instead of a compound planetary gear set assembly.

  As shown in FIGS. 9 to 11, the fixed housing (ground), the input shaft 70, the variator 30 having the first ring assembly 32 and the second ring assembly 33, the first sun gear 142, the first A first planetary gear set 140 having a first set 144 of planetary gears coupled to one sun gear 142 and drivingly engaged with a first ring gear 141, and a first carrier 143; A second planetary gear set 150 having a sun gear 152, a second set of planetary gears 154 coupled to the second sun gear 152 and drivingly engaged with the second ring gear 151, and a second carrier 153. The output shaft 80, the first selectable torque transmission device 161, the second selectable torque transmission device 162, and the third selectable torque transmission device 16. The input shaft 70 is fixedly connected to the first ring assembly 32 of the variator 30, and the second ring assembly 33 of the variator is fixedly connected to the first sun gear 142 and the second sun gear 152. The second carrier 153 is drivingly engaged with the first ring gear 141, the output shaft 80 is drivingly connected to the first ring gear 141, and the first selectable torque transmission device 161 (first brake) ) Establishes a first forward variable range (“mode 1”) of the overall transmission speed ratio by connecting the second ring gear 151 to the ground, and a second selectable torque transmission device 162 (clutch). Connects the first carrier 143 to the input shaft 70 to establish a second forward variable range (“mode 2”) of the overall transmission speed ratio, and a third selectable torque transmission device 63 (second brake) connects the first carrier 143 to the ground to establish a reverse side variable range (“REV”) of the overall transmission speed ratio, and the variator 30 determines the speed of the first ring assembly. A continuously variable transmission 100 is provided herein that establishes a control variable ratio between the speed of the second ring assembly and thereby adjusts the overall transmission speed ratio in any of the variable ranges.

  In some embodiments, the three selectable torque transmission devices include a first brake 161, a clutch 162, and a second brake 163.

  As shown in FIGS. 12 to 14, the fixed housing (ground), the input shaft 70, the variator 30 having the first ring assembly 32 and the second ring assembly 33, the first sun gear 142, the first A first planetary gear set 140 having a first set 144 of planetary gears coupled to one sun gear 142 and drivingly engaged with a first ring gear 141, and a first carrier 143; A second planetary gear set 150 having a sun gear 152, a second set of planetary gears 154 coupled to the second sun gear 152 and drivingly engaged with the second ring gear 151, and a second carrier 153. The output shaft 80, the first selectable torque transmission device 161, the second selectable torque transmission device 162, and the third selectable torque transmission device 1. The input shaft 70 is fixedly connected to the first ring assembly 32 of the variator, and the second ring assembly 32 of the variator is fixedly connected to the second ring gear 153 and the first sun gear 142. The first carrier 143 is drivingly engaged with the second carrier 153, the output shaft 80 is drivingly connected to the first ring gear 141, and the first selectable torque transmission device 161 (first brake). Connects the second sun gear 152 to the ground to establish the first forward variable range (“mode 1”) of the overall transmission speed ratio, and the second selectable torque transmission device 162 (clutch) The first carrier 143 is coupled to the input shaft 70 to establish the second forward variable range (“mode 2”) of the overall transmission speed ratio, and the third selectable torque transmission device 16. (Second brake) connects the second carrier to the ground 153 to establish a reverse side variable range (“REV”) of the overall transmission speed ratio, and the variator 30 operates at the speed of the first ring assembly 32. A continuously variable transmission 110 is provided herein that establishes a control variable ratio between the speed of the second ring assembly 33 and thereby adjusts the overall transmission speed ratio in any of the variable ranges.

  In some embodiments, the three selectable torque transmission devices include a first brake 161, a clutch 162, and a second brake 163.

  As shown in FIGS. 15 to 17, the fixed housing (ground), the input shaft 70, the variator 30 having the first ring assembly 32 and the second ring assembly 33, the first sun gear 142, the first A first planetary gear set 140 having a first set 144 of planetary gears coupled to one sun gear 142 and drivingly engaged with a first ring gear 141, and a first carrier 143; A second planetary gear set 150 having a sun gear 152, a second set of planetary gears 154 coupled to the second sun gear 152 and drivingly engaged with the second ring gear 151, and a second carrier 153. The output shaft 80, the first selectable torque transmission device 161, the second selectable torque transmission device 162, and the third selectable torque transmission device 1. 3, the input shaft 70 is fixedly connected to the first ring assembly 32 of the variator 30, and the second ring assembly 33 of the variator 30 is fixed to the first ring gear 141 and the second sun gear 152. Connected, the first sun gear 142 is drivingly engaged with the second ring gear 151, the output shaft 80 is drivingly connected to the second carrier 153, and the first selectable torque transmission device 161 (first The second ring gear 151 is connected to the ground to establish the first forward variable range (“mode 1”) of the overall transmission speed ratio, and the second selectable torque transmission device 162 ( Clutch) connects the first carrier 143 to the input shaft 70, establishes a second forward variable range ("mode 2") of the overall transmission speed ratio, and transmits a third selectable torque transmission. The device 163 (second brake) couples the first carrier to the ground 143 to establish a reverse variable range (“REV”) of the overall transmission speed ratio, and the variator 30 is connected to the first ring assembly 32. A continuously variable transmission 120 is provided herein that establishes a control variable ratio between the speed of the second ring assembly 33 and the speed of the second ring assembly 33, thereby adjusting the overall transmission speed ratio in any of the variable ranges. The

  In some embodiments, the three selectable torque transmission devices include a first brake 161, a clutch 162, and a second brake 163.

  In any one or more of the above-described embodiments, the variator 30 is a ball-type variator, and the variator 30 rotatably supports a plurality of swivel axles 34 that are rotatably disposed around a power transmission shaft. The first ring assembly 32 and the second ring assembly 33 each have a ball contact area that is in continuous contact with all of the balls. The carrier assembly moves in a controlled manner with a narrow range of angles relative to the variator housing to cause the swiveling axle to change orientation, thereby varying the speed between the first ring assembly and the second ring assembly. Change the ratio.

  In any one or more of the above embodiments, as the speed ratio of the variator between the first ring assembly and the second ring assembly increases, the overall transmission speed ratio within the first forward range increases. The overall transmission speed ratio in the second forward range decreases, and the overall transmission speed ratio in the reverse range becomes more negative.

  In some embodiments, the overall transmission speed ratio in the first forward range and the second forward range is the same for the variator speed ratio that is near the upper limit of the variator speed ratio range but is still in that range. And the second selectable torque transmission device may be synchronously engaged while in the first forward range, and the first selectable torque transmission device is synchronized while in the second forward range. A further fixed ratio transmission mode of operation that can be engaged and that does not transmit power through the variator is established by using the first selectable torque transmission device and the second selectable torque transmission device simultaneously. The

  In any one or more of the above-described embodiments, the transmission can be utilized in both front and rear wheel drive vehicles.

  In any one or more of the above-described embodiments, the transmission can selectively connect any two of the rotating elements of the first planetary gear set or the second planetary gear set, thereby It further includes an optional fourth clutch that rotates all at once and establishes a third forward range.

  In some embodiments, when the optional fourth clutch is engaged, the entire gear set rotates as a single unit, causing the transmission output speed to be equal to the output speed of the variator, The transmission speed ratio is increased, and all of the input power is transmitted to the output ring gear via the variator in the theoretical CVP range.

  Proceeding now to FIG. 18 and still referring to FIG. 11, in one embodiment, the continuously variable transmission 200 includes a stationary housing (ground) 20, an input shaft 70, a first ring assembly 32 and a second ring assembly. Variator 30 having a ring assembly 33, a first sun gear 42, a first set of planetary gears coupled to the first sun gear 42 and drivingly engaged with the first ring gear 41, and the planetary gears A first planetary gear set 40 having a first carrier 43 configured to support the first set, a second sun gear 92, a second sun gear 92, and a second ring A second planetary gear set 90 having a second set of planetary gears drivingly engaged with the gear 91 and a second carrier 93 configured to support the second set of planetary gears; An output shaft 80, the input shaft 70 is fixedly connected to the first ring assembly 32 of the variator 30, and the second ring assembly 33 of the variator 30 includes a first sun gear 42 and a second sun gear 92. The second carrier 93 is drivingly engaged with the first ring gear 41, the output shaft 80 is drivingly connected to the first ring gear 41, and the variator 30 is connected to the first ring assembly 32. Control variable ratio between the speed of the second ring assembly 33 and the speed of the second ring assembly 33, thereby adjusting the overall transmission speed ratio in any of the variable ranges.

  As shown in FIG. 18, an input shaft 70 that can be operatively connected to the rotational power source 25, and a first traction ring assembly 32 that contacts a plurality of balls 35 each having a tiltable rotation shaft 34. A variator assembly 30 having a second traction ring assembly 33 and having the first traction ring assembly 32 coupled to the input shaft 70, a first sun gear 42, a first carrier 43, and a first ring gear A first planetary gear set 40 having a second traction ring assembly 33 coupled to a first sun gear 42, a second sun gear 92, a second carrier 93, and a second ring. A second planetary gear set 9 having a gear 91 and having a second traction ring assembly 33 coupled to the second sun gear 91 And an interface shift sleeve assembly 250 having a first interface clutch 261 and a second interface clutch 262. The first interface clutch 261 can select the first ring gear 41 as the second carrier 93. A continuously variable transmission 200 is provided herein, wherein the second interface clutch 262 selectively couples the second ring gear 91 to the first carrier 43.

  In some embodiments, the first interface clutch 261 and the second interface clutch 262 include dog clutches.

  In some embodiments, the continuously variable transmission further includes a first selectable clutch 271 coupled to the first ring gear 41, and the first selectable clutch 271 includes the first ring gear 41. A non-rotating housing 20 is selectably connected.

  In some embodiments, the continuously variable transmission further includes a second selectable clutch 272 that is coupled to the input shaft 70, and the second selectable clutch 272 includes the input shaft 70 on the second carrier 93. Link selectably.

  In some embodiments, the power output is transmitted via the second ring gear 91.

  In some embodiments, the first selectable clutch 271 or the second selectable clutch 272 includes a friction clutch.

  In some embodiments, the continuously variable transmission is configured for a rear wheel drive vehicle.

  In some embodiments of the continuously variable transmission, the interface shift sleeve assembly 252 is radially disposed outside the first planetary gear set 40 and the second planetary gear set 90.

  In some embodiments of the continuously variable transmission, the interface shift sleeve assembly 252 includes a plurality of interfaces configured to selectively engage the mating surface with the first ring gear 41 and the second ring gear 91. Includes internal teeth.

  In some embodiments of the continuously variable transmission, the interface shift sleeve assembly 252 includes a plurality of internal teeth configured to selectively engage a mating surface with the first carrier 43 and the second carrier 93. including.

  In some embodiments, the engagement of the interface shift sleeve assembly 252 with the first ring gear 41 corresponds to the engagement of the interface shift sleeve assembly 252 with the second carrier 93.

  In some embodiments, the engagement of the interface shift sleeve assembly 252 with the second ring gear 91 corresponds to the engagement of the interface shift sleeve assembly 252 with the first carrier 43.

  In some embodiments, the continuously variable transmission further includes an output shaft 80.

  In some embodiments, the continuously variable transmission further includes a second rotatable shaft 72 coupled to the output shaft 80 and the second ring gear 91.

  In some embodiments, the continuously variable transmission further includes a power input interface 15. In some embodiments, the power input interface 15 includes a torque converter.

  In some embodiments, the continuously variable transmission is configured for a front wheel drive vehicle.

  Referring now to FIG. 19, an input shaft 70 that can be operatively coupled to the rotational power source 25, and a first traction ring 32 and a second that each contact a plurality of balls 35 having a rotatable shaft 34 that is tiltable. Variator assembly 30 having first traction ring assembly 32 coupled to input shaft 70, first sun gear 42, first carrier 43, and first ring gear 41. Then, the second planetary gear set 40 in which the second traction ring assembly 33 is connected to the first sun gear 42, the second sun gear 92, the second carrier 93, and the second ring gear 91 are connected. A second planetary gear set 90 having a second traction ring assembly 33 coupled to a second sun gear 92 and a first interface And an interface shift sleeve assembly 252 having E over scratch 261 and the second interface clutch 262, the continuously variable transmission 300 is provided herein.

  In some embodiments, the first interface clutch 261 selectably couples the first ring gear 41 to the second carrier 93.

  In some embodiments, the second interface clutch 262 selectably couples the second ring gear 91 to the first carrier 43.

  In some embodiments, the first interface clutch 261 and the second interface clutch 262 include dog clutches.

  In some embodiments, the continuously variable transmission further includes a direct connection to the rotational power source 25.

  In any one or more of the transmissions provided herein, the transmission further comprises a direct connection to a rotational power source. In some embodiments, the transmission further comprises an interface shift sleeve assembly having a first interface clutch and a second interface clutch, wherein one or both of the first interface clutch and the second interface clutch is a dog Has a clutch.

  In any one or more of the transmissions provided herein, the variator has traction fluid.

  A vehicle drive system comprising: a power source; one of the continuously variable transmissions described in the present specification that is drivingly engaged with the power source; and a vehicle output unit that is drivingly engaged with the continuously variable transmission. Provided herein. In some embodiments, the power source is drivingly engaged with the vehicle output.

  Provided herein is a vehicle comprising any of the continuously variable transmissions described herein.

  Provided herein is a method comprising providing any of the continuously variable transmissions described herein.

  Provided herein is a method comprising providing a vehicle drive train having any of the continuously variable transmissions described herein.

  Provided herein is a method comprising providing a vehicle having any of the continuously variable transmissions described herein.

  While preferred embodiments of the present invention have been shown and described herein, it will be apparent to those skilled in the art that such embodiments are provided by way of example only. Many variations, modifications, and alternatives will now occur to those skilled in the art without departing from the invention. It should be understood that various alternatives to the embodiments of the invention described herein can be utilized in practicing the invention. The following claims are intended to define the scope of the invention and thereby include the methods and structures in these claims and their equivalents.

Claims (42)

  1. A fixed housing (ground),
    An input shaft;
    A variator having a first ring assembly and a second ring assembly;
    A first planetary gear set having a first sun gear, a first set of planetary gears coupled to the first sun gear and drivingly engaged with a first ring gear, and a first carrier; ,
    A second planetary gear set having a second sun gear, a second set of planetary gears coupled to the second sun gear and drivingly engaged with a second ring gear, and a second carrier; ,
    A first selectable torque transmission device, a second selectable torque transmission device, and a third selectable torque transmission device;
    An output shaft and
    The input shaft is fixedly connected to the first ring assembly;
    The second ring assembly is fixedly connected to the first sun gear and the second sun gear;
    The second carrier is drivingly engaged with the first carrier;
    The output shaft is drivingly connected to the first ring gear and the second ring gear;
    The first selectable torque transmission device connects the first carrier and the second carrier to a ground to establish a first forward-side variable range of an overall transmission speed ratio,
    The second selectable torque transmission device connects the first carrier to the input shaft to establish a second forward variable range of the overall transmission speed ratio;
    The third selectable torque transmission device connects the first carrier and the second carrier to a ground to establish a reverse side variable range of the overall transmission speed ratio,
    The variator controls a variable speed ratio between the speed of the first ring assembly and the speed of the second ring assembly, thereby adjusting the overall transmission speed ratio in any of the variable ranges; Continuously variable transmission.
  2. The first selectable torque transmission device, the second selectable torque transmission device, and the third selectable torque transmission device are:
    A first brake;
    Clutch,
    The continuously variable transmission according to claim 1, further comprising a second brake.
  3. A fixed housing (ground),
    An input shaft;
    A variator having a first ring assembly and a second ring assembly;
    A first planetary gear set having a first sun gear, a first set of planetary gears coupled to the first sun gear and drivingly engaged with a first ring gear, and a first carrier; ,
    A second planetary gear set having a second sun gear, a second set of planetary gears coupled to the second sun gear and drivingly engaged with a second ring gear, and a second carrier; ,
    An output shaft;
    A first selectable torque transmission device coupled to the second sun gear and the stationary housing;
    A second selectable torque transmission device coupled to the first carrier and the input shaft;
    A third selectable torque transmission device coupled to the second carrier and the fixed housing;
    The input shaft is fixedly connected to the first ring assembly;
    The second ring assembly is fixedly connected to the second ring gear and the first sun gear;
    The first carrier is drivingly engaged with the second carrier;
    The output shaft is drivingly connected to the first ring gear;
    The engagement of the first selectable torque transmission device corresponds to a first forward variable range of the overall transmission speed ratio,
    The engagement of the second selectable torque transmission device corresponds to a second forward variable range of the overall transmission speed ratio,
    The engagement of the third selectable torque transmission device corresponds to the reverse side variable range of the overall transmission speed ratio,
    The variator controls a variable speed ratio between the speed of the first ring assembly and the speed of the second ring assembly, thereby adjusting the overall transmission speed ratio in any of the variable ranges; Continuously variable transmission.
  4. The first selectable torque transmission device, the second selectable torque transmission device, and the third selectable torque transmission device are:
    A first brake;
    Clutch,
    The continuously variable transmission according to claim 3, comprising a second brake.
  5. A fixed housing (ground),
    An input shaft;
    A variator having a first ring assembly and a second ring assembly;
    A first planetary gear set having a first sun gear, a first set of planetary gears coupled to the first sun gear and drivingly engaged with a first ring gear, and a first carrier; ,
    A second planetary gear set having a second sun gear, a second set of planetary gears coupled to the second sun gear and drivingly engaged with a second ring gear, and a second carrier; ,
    An output shaft;
    A first selectable torque transmission device coupled to the second ring gear and the ground;
    A second selectable torque transmission device coupled to the first carrier and the input shaft;
    A third selectable torque transmission device coupled to the first carrier and the ground;
    The input shaft is fixedly connected to the first ring assembly of the variator;
    The second ring assembly is fixedly connected to the first ring gear and the second sun gear;
    The first sun gear is drivingly engaged with the second ring gear;
    The output shaft is drivingly connected to the second carrier;
    The engagement of the first selectable torque transmission device corresponds to a first forward variable range of the overall transmission speed ratio,
    The engagement of the second selectable torque transmission device corresponds to a second forward variable range of the overall transmission speed ratio,
    The engagement of the third selectable torque transmission device corresponds to the reverse side variable range of the overall transmission speed ratio,
    The variator controls a variable speed ratio between the speed of the first ring assembly and the speed of the second ring assembly, thereby adjusting the overall transmission speed ratio in any of the variable ranges. Step transmission.
  6. Three of the first selectable torque transmission device, the second selectable torque transmission device, and the third selectable torque transmission device are:
    A first brake;
    Clutch,
    The continuously variable transmission according to claim 5, comprising a second brake.
  7. The variator is a ball variator, and the variator is
    A carrier assembly that rotatably supports a plurality of swivel axles arranged rotatably about a power transmission shaft;
    A plurality of swiveling axles each further rotatably supporting a ball;
    The first ring assembly and the second ring assembly each include a ball contact area in continuous contact with each of the balls;
    The carrier assembly moves in a controlled manner within a narrow range of angles to cause the plurality of swiveling axles to change orientation, whereby the variable speed between the first ring assembly and the second ring assembly. The continuously variable transmission according to any one of claims 1 to 6, wherein the ratio is changed.
  8. When the speed ratio of the variator increases,
    The overall transmission speed ratio within the first forward range increases;
    The overall transmission speed ratio within the second forward range decreases,
    The continuously variable transmission according to any one of claims 1 to 7, wherein the overall transmission speed ratio within a reverse range becomes more negative.
  9. If the speed ratio of the variator is near the upper limit of the range of the variable speed ratio, but still within the range,
    The overall transmission speed ratio in the first forward range and the second forward range is the same;
    The second selectable torque transmitting device is engaged synchronously while in the first forward range;
    The first selectable torque transmitting device is engaged synchronously while in the second forward range;
    9. A fixed ratio transmission mode of operation that does not transmit power through the variator is established by using the first selectable torque transmission device and the second selectable torque transmission device simultaneously. The continuously variable transmission described.
  10.   The continuously variable transmission according to any one of claims 1 to 9, wherein the continuously variable transmission is used in both a front wheel drive vehicle and a rear wheel drive vehicle.
  11.   Any two of the rotating elements of the first planetary gear set or the second planetary gear set are selectably connected, thereby rotating all of the rotating elements at once, and a third forward range. 6. The continuously variable transmission according to any one of claims 1, 3, or 5, further comprising an optional fourth clutch for establishing
  12.   When the fourth clutch is engaged, the whole of the first planetary gear set or the second planetary gear set rotates as a single unit, and the transmission output speed is equal to the output speed of the variator. The continuously variable transmission according to claim 11, wherein the entire transmission speed ratio is increased and all of the input power is transmitted to the output ring gear via the variator in a theoretical CVP range.
  13. A fixed housing;
    An input shaft;
    A variator having a first ring assembly and a second ring assembly;
    A first planetary gear set having a first sun gear, a first set of planetary gears coupled to the first sun gear and drivingly engaged with a first ring gear, and a first carrier; ,
    A second planetary gear set having a second sun gear, a second set of planetary gears coupled to the second sun gear and drivingly engaged with a second ring gear, and a second carrier; ,
    An output shaft and
    The input shaft is fixedly connected to the first ring assembly;
    The second ring assembly is fixedly connected to the first sun gear and the second sun gear;
    The second carrier is drivingly engaged with the first ring gear;
    The output shaft is drivingly connected to the first ring gear;
    The continuously variable transmission, wherein the variator controls a variable speed ratio between the speed of the first ring assembly and the speed of the second ring assembly, thereby adjusting the overall transmission speed ratio.
  14. An input shaft operably coupled to a rotational power source;
    A variator assembly having a first traction ring assembly and a second traction ring assembly in contact with a plurality of balls, each ball having a tiltable axis of rotation;
    A first planetary gear set having a first sun gear, a first carrier, and a first ring gear;
    A second planetary gear set having a second sun gear, a second carrier, and a second ring gear;
    An interface shift sleeve assembly having a first interface clutch and a second interface clutch;
    The first traction ring assembly is coupled to the input shaft;
    The second traction ring assembly is coupled to the first sun gear and the second sun gear;
    The first interface clutch selectively connects the first ring gear to the second carrier;
    The second interface clutch is a continuously variable transmission that selectively connects the second ring gear to the first carrier.
  15.   The continuously variable transmission according to claim 14, wherein the first interface clutch and the second interface clutch include a dog clutch.
  16.   15. A first selectable clutch coupled to the first ring gear, wherein the first selectable clutch selectively couples the first ring gear to a non-rotating housing. 15. The continuously variable transmission according to 15.
  17.   17. The system of claim 14, further comprising a second selectable clutch coupled to the input shaft, wherein the second selectable clutch selectively couples the input shaft to the second carrier. The continuously variable transmission according to item 1.
  18.   The continuously variable transmission according to claim 17, wherein the power output is transmitted via the second ring gear.
  19.   The continuously variable transmission according to claim 16 or 17, wherein the first selectable clutch or the second selectable clutch includes a friction clutch.
  20.   The continuously variable transmission according to any one of claims 14 to 19, wherein the interface shift sleeve assembly is radially disposed outside the first planetary gear set and the second planetary gear set.
  21.   21. The continuously variable transmission of claim 20, wherein the interface shift sleeve assembly includes a plurality of internal teeth that selectively engage a mating surface with the first ring gear and the second ring gear.
  22.   The continuously variable transmission of claim 21, wherein the interface shift sleeve assembly includes a plurality of internal teeth that selectively engage a mating surface with the first carrier and the second carrier.
  23.   The continuously variable transmission according to claim 21 or 22, wherein the engagement of the interface shift sleeve assembly with the first ring gear corresponds to the engagement of the interface shift sleeve assembly with the second carrier.
  24.   The continuously variable transmission according to claim 21 or 22, wherein the engagement of the interface shift sleeve assembly with the second ring gear corresponds to the engagement of the interface shift sleeve assembly with the first carrier.
  25.   The continuously variable transmission according to claim 20, further comprising an output shaft.
  26.   26. The continuously variable transmission of claim 25, further comprising a second rotatable shaft coupled to the output shaft and the second ring gear.
  27.   26. The continuously variable transmission of claim 25, wherein the output shaft is operably coupled to a differential.
  28.   The continuously variable transmission according to claim 14 or 20, further comprising a power input interface.
  29.   The continuously variable transmission according to claim 28, wherein the power input interface includes a torque converter.
  30. An input shaft operably coupled to a rotational power source;
    A variator assembly having a first traction ring assembly and a second traction ring assembly in contact with a plurality of balls, each ball having a tiltable axis of rotation;
    A first planetary gear set having a first sun gear, a first carrier, and a first ring gear;
    A second planetary gear set having a second sun gear, a second carrier, and a second ring gear;
    An interface shift sleeve assembly having a first interface clutch and a second interface clutch;
    The first traction ring assembly is coupled to the input shaft;
    The second traction ring assembly is coupled to the first sun gear;
    The continuously variable transmission, wherein the second traction ring assembly is coupled to the second sun gear and the interface shift sleeve assembly.
  31.   31. The continuously variable transmission according to claim 30, wherein the first interface clutch selectively connects the first ring gear to the second carrier.
  32.   32. The continuously variable transmission according to claim 30 or 31, wherein the second interface clutch selectively connects the second ring gear to the first carrier.
  33.   The continuously variable transmission according to any one of claims 30 to 32, wherein the first interface clutch and the second interface clutch include a dog clutch.
  34.   The continuously variable transmission according to any one of claims 14, 20, and 30, further comprising a direct connection portion to the rotational power source.
  35.   15. The interface shift sleeve assembly further comprising a first interface clutch and a second interface clutch, wherein one or both of the first interface clutch and the second interface clutch comprises a dog clutch. Continuously variable transmission.
  36.   The continuously variable transmission according to any one of claims 1, 3, 5, 13, 14, 20, or 30, wherein the variator has a traction fluid.
  37.   37. A continuously variable transmission according to any one of claims 1 to 36, which is drivingly engaged with the power source, and a vehicle output unit that is drivingly engaged with the continuously variable transmission. , Vehicle drive system.
  38.   38. The vehicle drive system according to claim 37, wherein the power source is drivingly engaged with the vehicle output unit.
  39.   A vehicle comprising the continuously variable transmission according to any one of claims 1 to 36.
  40.   37. A method comprising providing a continuously variable transmission according to any one of claims 1-36.
  41.   39. A method comprising providing a vehicle drive train according to claim 37 or 38.
  42.   40. A method comprising providing the vehicle of claim 39.
JP2017530122A 2014-12-08 2015-12-04 Three-mode planetary mechanism continuously variable transmission for front wheel drive and rear wheel drive Pending JP2017537285A (en)

Priority Applications (5)

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US201462089126P true 2014-12-08 2014-12-08
US62/089,126 2014-12-08
US201562144751P true 2015-04-08 2015-04-08
US62/144,751 2015-04-08
PCT/US2015/064087 WO2016094254A1 (en) 2014-12-08 2015-12-04 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission

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