3-mode front wheel drive and rear wheel drive continuously variable planetary transmission

Abstract

A front wheel drive or rear wheel drive continuously variable transmission is provided having an input shaft, an output shaft, a continuously variable tilting ball planetary variator, a compound planetary gearset assembly having first, second, third, and fourth rotating elements, and a plurality of torque transmitting devices. The compound planetary gearset assembly has a simple single pinion gearset and a compound double pinion gearset, having fixedly connected planetary carriers and fixedly connected ring gears, creating a joint planetary gear carrier and joint ring gear. The outer planetary gears engage the ring gear which drives the output shaft. Selective torque transmitting devices include clutches and braking clutches.

Claims

1. A continuously variable transmission comprising: a stationary housing; an input shaft; an output shaft; a gearset having a first rotating element, a second rotating element, a third rotating element, and a fourth rotating element; a variator assembly having a first ring assembly and a second ring assembly; a first clutch capable of engaging the fourth rotating element to the stationary housing; a second clutch capable of engaging the input shaft to the second rotating element; and a third clutch capable of engaging the second rotating element to the stationary housing; wherein the input shaft is fixedly connected with the first ring assembly, the second ring assembly is fixedly connected with the first rotating element, the output shaft is fixedly connected with the third rotating element, engagement of the first clutch establishes a first forward variable range within an overall transmission speed ratio, engagement of the second clutch establishes a second forward variable range within the overall transmission speed ratio, engagement of the third clutch establishes a reverse variable range within the overall transmission speed ratio, and the variator controls a variable speed ratio between speeds of the first ring assembly and the second ring assembly, thereby adjusting the overall transmission speed ratio within any of the first forward variable range, the second forward variable range or the reverse variable range.

2. The transmission of claim 1, wherein the gearset is a compound planetary gearset, wherein the third rotating element is a ring gear, wherein the second rotating element is a carrier assembly rotatably supporting an outer set of long pinion gears meshing with the ring gear and an inner set of short pinion gears meshing with the outer set of long pinion gears, wherein the first rotating element is a first sun gear meshing with the outer set of long pinion gears, and wherein the fourth rotating element is a second sun gear meshing with said the inner set of short pinion gears.

3. The transmission of claim 1, wherein the gearset is a Ravigneaux compound planetary gearset.

4. The transmission of claim 1, wherein the variator assembly is a ball-type variator assembly comprising; a carrier assembly rotatably supporting a plurality of pivoting axles rotatably disposed about the transmission axis, the pivoting axles each rotatably supporting a ball; wherein the first ring assembly and the second ring assembly each comprising a ball contact area in continuous contact with each of the balls, and wherein the carrier assembly moves in a controlled fashion through a range of angles in order to cause the pivoting axles to change orientation, thus varying the variable speed ratio between the first ring assembly and the second ring assembly.

5. The transmission of claim 4, wherein, as the variable speed ratio increases, the overall transmission speed ratio within the first forward variable range increases; the overall transmission speed ratio within the second forward variable range decreases; and the overall transmission speed ratio within the reverse variable range decreases.

6. The transmission of claim 5, wherein when the variable speed ratio is within a variable speed ratio range; the overall transmission speed ratio in the first forward variable range and the second forward variable range is the same; the second clutch can be synchronously engaged while in the first forward variable range; the first clutch can be synchronously engaged while in the second forward variable range; and a fixed-ratio transmission operating mode which transmits no power through the variator is established by simultaneous application of the first clutch and second clutch.

7. The transmission of claim 6, wherein said second clutch is a dog clutch.

8. The transmission of claim 1, further comprising a fourth clutch which selectably connects any two of the gearset's rotating elements, thus causing all of the rotating elements to rotate in unison, and establishing a third variable forward range.

9. The transmission of claim 8, wherein the fourth clutch is a dog clutch.

10. The transmission of claim 1, wherein the first clutch and the third clutch are braking clutches.

11. The transmission of claim 1 wherein the transmission is capable of being utilized in both front wheel drive and rear wheel drive vehicles.

12. The transmission of claim 1 wherein the variator comprises a traction fluid.

13. A vehicle comprising the transmission of claim 1.

14. A method comprising providing a vehicle comprising the transmission of claim 13.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) 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:

(2) FIG. 1 is a stick diagram of a rear wheel drive embodiment of the 3-mode transmission as described herein.

(3) FIG. 2 is a stick diagram of a front wheel drive embodiment of the 3-mode transmission as described herein.

(4) FIG. 3 is a lever diagram of an embodiment of the 3-mode transmission as described herein.

(5) FIG. 4 is a lever diagram of another embodiment of the 3-mode transmission showing an optional sync clutch, as described herein.

(6) FIG. 5 is an alternate configuration view of the compound gear set of the 3-mode transmission.

(7) FIG. 6 is another alternate configuration view of the compound gear set of the 3-mode transmission.

(8) FIG. 7 is a side sectional view of a ball-type variator;

(9) FIG. 8 is a magnified, side sectional view of a ball of a variator of FIG. 7 having a symmetric arrangement of a first ring assembly and a second ring assembly

DETAILED DESCRIPTION OF THE INVENTION

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

(11) Continuously Variable Transmissions or CVTs are of many types: belts with variable pulleys, toroidal, and conical, for non-limiting example. The principle of a CVT is that it enables the engine to run at its most efficient rotation speed by changing steplessly the transmission ratio in function of the speed of the car and the torque demand (throttle position) of the driver. If needed, for example when accelerating, the CVT is configured to also shift to the most optimum ratio providing more power. A CVT is configured to change the ratio from the minimum to the maximum ratio without any interruption of the power transmission, as opposed to the opposite of usual transmissions which require an interruption of the power transmission by disengaging to shift from one discrete ratio to engage the next ratio.

(12) Provided herein are configurations of CVTs based on a ball type variators, also known as CVP, for constant variable planetary. Basic concepts of a ball type Continuously Variable Transmissions are described in US2006084549 and AU2011224083A1, incorporated herein by reference in their entirety. Such a CVT, adapted herein as described throughout this specification, comprises a number of balls 997, depending on the application, two discs with a conical surface contact with the balls, as input 995 and output 996, and an idler 999 as shown on FIG. 7. The balls are mounted on axes 998, themselves held in a cage or carrier allowing changing the ratio by tilting the balls' axes. Other types of ball CVTs also exist, like the one produced by Milner, but are slightly different.

(13) The working principle of such a CVP of FIG. 7 is shown on FIG. 8. The CVP itself works with a fraction 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. By tilting the balls' axes, the ratio can be changed between input and output. When the axis is horizontal 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 balls' axes are tilted at the same time with a mechanism included in the cage.

(14) Provided herein is a front wheel drive or rear wheel drive continuously variable transmission configured to optimize speed ratios to provide good, tunable overall ratios (OAR) and mode overlap, while avoiding the high pinion or carrier speeds and other disadvantages of existing 3-mode power flows.

(15) As shown in the lever diagram of FIG. 3, provided herein is a front wheel drive (or rear wheel drive) continuously variable transmission 10 comprising a stationary housing (ground), an input shaft 70, an output shaft 80, a gearset having first 61, second 63, third 66, and fourth 62 rotating elements, a variator assembly 30 having first and second rotating elements and three selectable torque transmitting devices (“clutches”) 21, 22, 23; wherein the input shaft is fixedly connected with the first rotating element of the variator assembly 30, the second rotating element of the variator assembly is fixedly connected with the first element of the gearset 61, the output shaft 80 is fixedly connected with the third element 66 of the gearset; the first clutch 21 connects the fourth element of the gearset 62 to ground, establishing a first forward variable range of overall transmission speed ratios; the second clutch 22 connects the input shaft 70 to the second element of the gearset 63, establishing a second forward variable range of overall transmission speed ratios; the third clutch 23 connects the second element of the gearset 63 to ground, establishing a reverse variable range of overall transmission speed ratios; and wherein, the variator establishes a controlled, variable ratio between the speeds of its first and second rotating elements, thereby adjusting the overall transmission speed ratio within any of said variable ranges.

(16) In some embodiments, such as described in FIGS. 1 and 5, the gearset is a compound planetary gearset having rotating elements comprising a first (“single-pinion”) planetary gearset 40 comprising; a first ring gear 41, a first sun gear 42, and a first carrier assembly 43, and, a second (“double-pinion”) planetary gearset 50, having rotating elements comprising; a second ring gear 51, a second sun gear 52, and a second carrier assembly 53; wherein the first carrier assembly 43 of the first planetary gearset 40 rotatably supports a first single set of pinions 44 which engage said single-pinion planetary gearset first ring gear 41 and said single-pinion planetary gearset first sun gear 42; and, the second carrier assembly 53 of the double-pinion planetary gearset 50 rotatably supports, a second set of pinions 54 which engage said double-pinion planetary gearset second sun gear 52, and a third set of pinions 55 which engage said second set of pinions 54 and said double-pinion planetary gearset second ring gear 51; and wherein, the first and second carrier assemblies 43, 53 of the first and second planetary gearsets 40, 50 are fixedly connected 45; the first ring gear 41 of the first planetary gearset 40 and the second ring gear 51 of the second planetary gearset 50 are fixedly connected 46 and wherein, the first rotating element of the gearset is said first sun gear 42, the second rotating element of the gearset is said fixedly connected carrier assemblies 45, the third rotating element of the gearset is said fixedly connected ring gears 46, and the fourth rotating element of the gearset is said second sun gear 52.

(17) In some embodiments, as shown in FIGS. 2 and 6, the gearset is a compound planetary gearset 60 comprising a ring gear 66, a carrier assembly 63 rotatably supporting an outer set of long pinion gears 64 in mesh with said ring gear 66 and an inner set of short pinion gears 65 in mesh with said outer set of long pinion gears 64, a first sun gear 61 meshing with said outer set of long pinion gears 64, and a second sun gear 62 meshing with said inner set of short pinion gears 65; and wherein, the first rotating element of the gearset is said first sun gear 61, the second rotating element of the gearset is said carrier assembly 63, the third rotating element of the gearset is said ring gear 66, and the fourth rotating element of the gearset is said second sun gear 62. In some embodiments, the gearset 60 is a Ravigneaux compound planetary gearset.

(18) As illustrated in FIG. 7, a variator is a system that uses a set of rotating and tilting balls in a carrier that is positioned between an input ring and an output ring. Tilting the balls changes their contact diameters and varies the speed ratio. Contacting a rotating sphere at two different locations relative to the sphere's rotational axis will provide a “gear ratio”, which can range from underdrive to overdrive depending on the location of the contact points for input and output torque and speed. As a result, the variator system offers continuous transition to any ratio within its range. The gear ratio is shifted by tilting the axes of the spheres in a continuous fashion, to provide different contact radii, which in turn drive the input and output rings, or discs.

(19) The variator, as noted above, has multiple balls to transfer torque through multiple fluid patches. The balls are placed in a circular array around a central idler (sun) and contact separate input and output traction rings at engagement points about the balls. This configuration allows the input and output to be concentric and compact. The result is the ability to sweep the transmission through the entire ratio range smoothly, while in motion, under load, or stopped.

(20) The variator itself works with a traction fluid. The traction fluid is located in the variator for lubrication and traction. When this fluid undergoes high contact pressures under rolling contact between the two very hard elements, the balls and the rings, the fluid undergoes a near-instantaneous phase transition to an elastic solid. This is also known as elastohydrodynamic lubrication (EHL). Within this patch of traction the molecules of the fluid stack up and link to form a solid, through which shear force and thus torque can be transferred. Note that the rolling elements are actually not in physical contact when the elements are rotating.

(21) The lubricant between the ball and the conical rings acts as a solid at high pressure, transferring the power from the first ring assembly 32 (input of the variator), through the variator balls 35, to the second ring assembly 33 (output of the variator). As illustrated in FIG. 8, by tilting the variator balls' axes 34, the ratio is changed between input and output. When the axis of each of the variator balls is horizontal the ratio is one, when the axis is tilted the distance between the axis and the contact point change, modifying the overall ratio, between underdrive and overdrive. All the variator balls' axles are tilted at the same time and same angle with a mechanism included in the cage.

(22) The embodiments of the present invention as described herein will find many applications. For example, although reference is made to vehicular applications, the continuously variable transmission as described herein can be used in many applications such as bicycles, motorized vehicles, wind turbines, and power tools, for example. The embodiments of the present invention as described herein will find applications in front-wheel drive or rear-wheel drive transmissions for both On- and Off-highway vehicles.

(23) As previously described and now shown in FIGS. 1 and 2, in some embodiments of the CVP transmission 10, the variator is a ball-type variator 30 comprising; a carrier assembly 31 rotatably supporting a plurality of pivoting axles 34 rotatably disposed about the transmission axis, said pivoting axles 34 each in turn further rotatably supporting a ball 35; and wherein the first and second ring assemblies 32, 33, each comprising a ball contact area in continuous contact with all of said balls. The first rotating element of the variator is first ring assembly 32, the second rotating element of the variator is said second ring assembly 32; and the carrier assembly 31 moves in controlled fashion through a small range of angles as previous illustrated in FIG. 8, with respect to the variator housing in order to cause the pivoting axles 34 to change orientation, thus changing the speed ratio between said first and second rings assemblies.

(24) In some embodiments of the transmission, as the variator speed ratio between the first and second assembly rings increases, the overall transmission speed ratio within said first forward range increases; the overall transmission speed ratio within said second forward range decreases; and the overall transmission speed ratio within said reverse range becomes more negative. In still other embodiments, the transmission, having a variator speed ratio which is near the upper end of the variator speed ratio range but still within said range, may have overall transmission speed ratios in the first and second forward ranges that are the same; wherein the second clutch can be synchronously engaged while in the first forward range; the first clutch can be synchronously engaged while in the second forward range; and an additional, fixed-ratio transmission operating mode, which transmits no power through the variator, is established by simultaneous application of the first and second clutches. The fixed ratio operating mode is further describes as the intersection of the 1st and 2nd modes; wherein, if both clutches 1 and 2 are locked, then the variator in theory doesn't need to transmit any power.

(25) In still other embodiments, as illustrated in FIGS. 1 and 4, the transmissions may further comprise an optional fourth clutch 24 which selectably connects any two of the gearset's four rotating elements, thus causing all of said elements to rotate in unison, and establishing a third forward range. When engaged, the entire gearset rotates as a single unit, and thus causing the transmission output speed to be equal to the variator output speed, extending the transmission overall ratio, and passing all of the input power through the variator to the ring gear in a pure CVP range between 0.5 and 1.8. Like the first forward and reverse modes, this optional third mode passes all of the input power through the variator, so it is not generally as efficient as the second mode, but allows higher transmission output speed ratios.

(26) While preferred embodiments of the present invention have been shown and described herein, it will be obvious to those skilled in the art that such embodiments are provided by way of example only. Numerous variations, changes, and substitutions 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 may be employed in practicing the invention. It is intended that the following claims define the scope of the invention and that methods and structures within the scope of these claims and their equivalents be covered thereby.