Ball type CVT with output coupled powerpaths

Information

  • Patent Grant
  • 10088026
  • Patent Number
    10,088,026
  • Date Filed
    Thursday, February 2, 2017
    7 years ago
  • Date Issued
    Tuesday, October 2, 2018
    6 years ago
Abstract
Systems, devices, and methods are provided for the transmission of power in motor vehicles. Power can be transmitted in a smoother and more efficient manner, with smaller and even less mechanical components, by splitting torque into two or more torque paths. A power transmission apparatus comprises a power input shaft, a planetary gear set coupled to the power input shaft, and a variator, such as a continuously variable transmission (CVT), coupled to the gear set. The various components of the planetary gear set and the variator are arranged such that torque is split between two or more torque paths and then recombined before power is output to a gear box and a differential of the motor vehicle.
Description
BACKGROUND OF THE INVENTION

Automatic and manual transmissions are commonly used on automobile vehicles. Those transmissions become more and more complicated since the engine speed has to be adjusted to limit the consumption and the emissions of cars. This finer control of the engine speed in usual transmissions is typically done by adding gears and increasing the overall complexity and cost. 6-speed manual transmissions then become frequent as are 8 or 9 speed automatic transmissions.


SUMMARY OF THE INVENTION

Systems, devices, and methods are provided for the transmission of power, particularly in motor vehicles. According to various embodiments of the disclosure, power can be transmitted in a smoother and more efficient manner, typically with smaller and even less mechanical components, by splitting torque into two or more torque paths. The apparatus described herein, or obvious to one of skill in the art upon reading this disclosure, may be used in a transaxle or any other type of transmission.


An aspect of the disclosure provides an apparatus for transmitting power. This apparatus comprises a power input shaft, a planetary gear set, and a variator, such as a continuously variable transmission (CVT). Aspects of the CVTs are described in US2006084549 or AU2011224083A1, incorporated herein by reference in their entirety. The planetary gear set is engaged with the power input shaft, typically from an internal combustion engine. The variator is engaged with the gear set. The apparatus, and in particular the configuration of the planetary gear set and the variator, is configured to split torque between a first torque path and a second torque path.


The variator may comprise an input ring and an output ring. The planetary gear set may comprise a set of planet gears, a sun gear engaged with the set of planet gears and with the input ring of the variator, a carrier engaged with the power input shaft and with the set of planet gears, and a ring gear engaged with the set of planet gears and with the output ring of the variator. The first torque path may pass from the power input shaft to the carrier, to the planet gears, to the sun gear, to the input ring, to the output ring of the variator, and then to the ring gear of the planetary gear set. The second torque path may pass from the power input shaft to the carrier, to the planet gears, and then to the ring gear of the planetary gear set. In some embodiments, a gear box for outputting power from the apparatus may be coupled to the planetary gear set. The gear box may be coupled to the ring of the planetary gear set and to a differential of a motor vehicle. The gear box may be, for example, a three speed gear box.


Another aspect of the disclosure provides a method of transmitting power. An input shaft, typically from an internal combustion engine, is driven. Torque from the input shaft is split between a first torque path and a second torque path. The first and second torque paths are combined to form a single output (i.e., power-split configuration). The first and second torque paths pass through various components of a planetary gear set and a variator coupled to the planetary gear set as described herein. The variator may comprise a continuously variable transmission (CVT). The first torque path may, for example, pass from the power input shaft to a carrier of the planetary gear set, to planet gears of the planetary gear set, to a sun gear of the planetary gear set, to an input ring of the variator, to an output ring of the variator, and then to a ring gear of the planetary gear set. The second torque path may, for example, pass from the power input shaft to the carrier of the planetary gear set, to the planet gears of the planetary gear set, and then to the ring gear of the planetary gear set.


Yet another aspect of the disclosure provides an apparatus for power transmission. The apparatus comprises a power input shaft, an input planetary gear set engaged with the power input shaft, a variator engaged with the input gear set, an output planetary gear set engaged with the variator, and one or more clutches and brake for switching between a plurality of operational modes of the power transmission apparatus. The apparatus is configured to split torque between a plurality of torque paths.


The variator may comprise an input ring and an output ring, and may be a continuously variable transmission (CVT). The input planetary gear set may comprise a set of input planet gears, an input sun gear engaged with the input planet gears and with the input ring of the variator, an input carrier engaged with the input planet gears and with the power input shaft, and an input ring engaged with the input planet gears. The output planetary gear set may comprise a set of output planetary gears, an output sun gear engaged with the power input shaft and with the output planet gears, an output carrier engaged with the output planet gears and with a gear box for outputting power from the apparatus, and an output ring engaged with the output planet and with the output ring of the variator. The power transmission apparatus may further comprise a counter shaft engaging the input ring and the output ring gears of the two planetary gear sets. The one or more clutches may comprise a first clutch and a second clutch. The first clutch may be configured to be engaged to engage the output sun gear with the output ring of the variator. The second clutch may be configured to be engaged to engage the power input shaft with the output sun gear. The power transmission apparatus may further comprise a brake for holding the output sun to achieve an additional operation mode of the power transmission apparatus. The power transmission apparatus may further comprise a gear box, such as a three speed gear box, coupled to the output carrier of the output planetary gear set as well as to a differential of a motor vehicle.


The plurality of operational modes of the power transmission apparatus may comprise a first mode, a second mode, and a third mode. The first, second, and third modes may comprise various continuously variable transmission (CVT) modes. The first mode may be selected by engaging the brake while releasing the first and second clutch. The second mode may be selected by engaging the second clutch while releasing the brake and the first clutch. The third mode may be selected by engaging the first clutch while releasing the brake and the second clutch.


In this embodiment, torque may be split into two paths—a first path through the variator and a second path through the countershaft in the first and third modes. Torque may also instead be split into three paths—a first path through the variator, a second path through the countershaft, and a third path between the power input shaft and the output sun gear of the output planetary gear set in the second mode.


Provided herein is a vehicle comprising the power transmission apparatus of any of embodiment described herein, or obvious to one of skill in the art upon reading the disclosures herein. Embodiments of the power transmission apparatus (variable transmission) described herein or that would be obvious to one of skill in the art upon reading the disclosure herein are contemplated for use in a variety of vehicle drivelines. For non-limiting example, the variable transmissions disclosed herein may be used in bicycles, mopeds, scooters, motorcycles, automobiles, electric automobiles, trucks, sport utility vehicles (SUV's), lawn mowers, tractors, harvesters, agricultural machinery, all terrain vehicles (ATV's), jet ski's, personal watercraft vehicles, airplanes, trains, helicopters, buses, forklifts, golf carts, motorships, steam powered ships, submarines, space craft, or other vehicles that employ a transmission.


While the figures and description herein are directed to ball-type variators (CVTs), alternate embodiments are contemplated another version of a variator (CVT), such as a Variable-diameter pulley (VDP) or Reeves drive, a toroidal or roller-based CVT (Extroid CVT), a Magnetic CVT or mCVT, Ratcheting CVT, Hydrostatic CVTs, Naudic Incremental CVT (iCVT), Cone CVTs, Radial roller CVT, Planetary CVT, or any other version CVT.


In some embodiments, the power transmission apparatus further comprises a traction fluid.


INCORPORATION BY REFERENCE

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





BRIEF DESCRIPTION OF THE DRAWINGS

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. 1 is a side sectional view of a continuously variable planetary (CVP) variator;



FIG. 2 is a magnified, side sectional view of a ball and ring of the CVP variator of FIG. 1;



FIG. 3 is a block diagram of a continuously variable transmission (CVT) used in an automobile;



FIG. 4 is a block diagram of a continuously variable transmission (CVT) according to an embodiment of the present disclosure used in an automobile;



FIG. 5 is a graph of a speed diagram of the CVT of FIG. 4;



FIG. 6 is a block diagram of a continuously variable transmission (CVT) according to another embodiment of the present disclosure used in an automobile;



FIG. 7 is a graph of a speed diagram of an input planetary gear of the CVT of FIG. 6; and



FIG. 8 is a graph of a speed diagram of an output planetary gear of the CVT of FIG. 6 in its different modes.





DETAILED DESCRIPTION OF THE INVENTION

Besides automatic and manual transmissions commonly used on automobile vehicles are developed Continuously Variable Transmissions or CVTs. Those CVTs are of many types: belts with variable pulleys, toroidal, conical, etc. 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. If needed for example when accelerating, the CVT can also shift to a ratio providing more power. A CVT can change the ratio from the minimum to the maximum ratio without any interruption of the power transmission, at the opposite of usual transmissions which require an interruption of the power transmission by disengaging to shift of ratio. A specific use of CVTs is the Infinite Variable Transmission or IVT. Where the CVT is limited at positive speed ratios, the IVT configuration can perform a neutral gear and even reverse steplessly. A CVT can be used as an IVT in some driveline configurations.


In many currently used motor vehicle transmissions, including manual transmissions, automatic transmissions, and CVTs, power and torque are not transmitted in a smooth or efficient manner. This can reduce fuel efficiency and can result in an unsmooth ride. Therefore, improved motor vehicle transmissions for smooth and efficient power and torque transmission are desired.


Within this disclosure, we introduce new driveline configurations based on a ball type CVT, also known as CVP, for constant variable planetary, for which Fallbrook Technologies, Inc. has applied for patents under the references US20060845449P and AU2011224083A1. This CVT comprises of a certain number of balls 997 (for example, 3-15 balls), depending on the application, two discs 995, 996 with a conical surface contact with the balls 997, as input 995 and output 996, and an idler 999 as shown on FIG. 1. The balls are mounted on axles 998, themselves hold in a cage or carrier allowing changing the ratio by tilting the ball's axes. An idler 999 sits below the balls in the cage. Other types of ball CVTs also exist, such as the one produced by Milner but are slightly different.


The working principle is shown on FIG. 2. The CVP itself works with a traction fluid. The lubricant between the ball and the conical rings acts as solid at high pressure, transferring the power from the input ring, through the balls, to the output ring. By tilting the ball's axles, the ratio can be changed between input and output. When the axis is horizontal the ratio is one (1:1), when the axis is tilted the distance between the axis and the contact point change, modifying the overall ratio (input radius>output radius=underdrive; input radius<output radius=overdrive). All the ball's axles are tilted at the same time with a mechanism included in the cage.


In a car, the CVT 103 includes a CVP (continuously variable planetary) and is used to replace traditional transmission and is located between the engine 100 and the differential 102 as shown on FIG. 3. A torsional damper 101 has to be introduced between the engine and the CVT 103 to avoid transferring torque peaks and vibrations that could seriously damage the CVT 103. In some configurations, this damper 101 can be coupled with a clutch for the starting function.


One configuration depicted in FIG. 4 uses a planetary gearset 8 to split the torque between two different paths. A part of the power will pass through the CVP 5 while the other part of it will pass directly from the planetary gearset 8 to the output through a mechanical path with higher efficiency. This power splitting allows a relatively small CVP and increases the native efficiency of the transmission. The central part of that configuration is the variator 5 described previously in the document. A ball ramp on each side of the variator provides the clamping force necessary to transfer the torque.


This configuration uses only one mode performing CVP function. To extend the speed range in the low speed and reverse area, a three speed gearbox 22 can be added after the CVP. Since this configuration does not have an IVP mode, a slipping clutch or a torque converter is optionally used to allow the start from standstill.


The internal combustion engine (ICE) is linked to the carrier 3 which in turn is linked to the planets 1 of the planetary gearset 8. The sun 2 of the planetary gearset 8 is connected to the variator input ring 6. The ring 4 of the planetary gearset 8 is linked to the variator output ring 7. This common ring 7 is connected to a three speed gearbox increasing the spread and allowing higher reverse speeds.



FIG. 5 shows the speed diagram of the planetary gearset 8. The three horizontal axes represent respectively, from the bottom to the top, the sun rotation speed, the carrier rotation speed and the ring rotation speed. The carrier is the input and typically always turns at ICE speed. The ring is the output and is linked to a three speed gearbox. The output speed achievable is noted on the top horizontal axis in diagonal shading between the two dotted diagonal lines. The dashed area noted on the top horizontal axis can be covered by the additional gearbox. The dotted area noted on the top horizontal axis has to be covered by a slipping clutch or a torque converter.


This device is able to change continuously its ratio to provide the best ratio achievable for the engine in function of the objectives of consumption or power. In a manual or automatic transmission, only some predetermined and discrete ratios are available and an interruption of the power transmission is needed to shift of ratio. Generally, the power interruptions in this device only occur during gear shifting of the additional gearbox. Other advantages of this configuration are that a very small variator can be chosen; spread is similar to a traditional gearbox if an additional (smaller) gearbox is added and the native efficiency of the transmission is increased by using the CVP in a powersplit device, therefore letting a part of the power passing through a more efficient mechanical path. Native efficiency will be high, because the variator input ring is connected to the sun, where the torque is lower, so more power is transmitted through the mechanical path (the ring).


Another embodiment configuration (depicted in FIG. 6) uses two planetary gearsets (input planetary gearset 10, output planetary gearset 12) to split the torque between different paths. The input planetary gearset 10 includes a planet 1a, a sun 2a, a carrier 3a, and a ring 4a. Similarly, the output planetary gearset 12 includes a planet 1b, a sun 2b, a carrier 3b, and a ring 4b. A part of the power will pass through the CVP 5 while the other part of it will pass to the output through a mechanical path with higher efficiency. Two clutches (first clutch 16, second clutch 18) and one brake 14 may be needed to have three different CVP modes. This power splitting allows to have a smaller CVP and to increase the native efficiency of the transmission. The central part of that configuration is the variator described previously in the document. A ball ramp on each side of the variator provides the clamping force necessary to transfer the torque.


There exist three modes performing a CVP function. To allow forward low speeds and reverse speeds, a three speed gearbox is added after the CVP. Since this configuration does not have an IVP mode, a slipping clutch or a torque converter can be used to allow starting from standstill and low speeds.


The ICE is linked to the carrier 3a of the input planetary gearset 10 and can be linked to the sun 2 of the output planetary gearset 12 through a second clutch 18. The sun 2a of the input planetary gearset 10 is linked to the variator input ring while the variator output ring is connected to the ring 4b of the output planetary gearset 12. Both rings 4a, 4b of the two planetaries gearsets 10, 12 respectively are linked by means of a countershaft 20. The variator output ring can also be connected to the output planetary sun 2b by engaging a first clutch 16. A brake 14 allows holding the output planetary sun 2b to perform an additional mode. The output is made by the carrier 3b of the output planetary and is directly linked to an additional three speed gearbox 22.


The three modes are selected by engaging one of the two clutches 16, 18 or brake 14 and releasing the two others. The first mode (CVP1) is obtained by engaging the brake 14, thus holding the sun 2b of the output planetary gearset 12 fixed. The second mode (CVP2) is selected by engaging the second clutch 18 and releasing the others, while the third mode (CVP3) is selected by engaging the first clutch 16. In the first and third mode, a part of the power is passing through the CVP 5 and a part of it is passing through the countershaft 20. In the second mode (CVP2), an additional power path is created between the ICE and the sun 2b of the output planetary gearset 12, thus splitting the power twice. The output planetary gearset 12 combines those different paths to a single output on its carrier 3b.



FIG. 7 shows the speed diagram of the input planetary gearset 10. The three horizontal axes represent respectively, from the bottom to the top, the sun 2a rotation speed, the carrier 3a rotation speed and the ring 4a rotation speed. The carrier a of the input planetary gearset 10 is directly connected to the ICE. The ring 4a speed is determined in function of the CVP ratio and is then directly applied to the output planetary ring 4b through the countershaft 20.



FIG. 8 shows the speed diagram of the output planetary gearset 12 for the three modes. This figure shows for mode CVP1, the sun 2b is held by the brake 14 and the output speed achievable can be observed on the carrier 3b axis. Mode CVP2 is selected by connecting the sun 2b of the output planetary gearset 12 to the ICE. The output speed achievable by doing this is shown on the carrier 3b axis with the text CVP2. Finally, mode CVP3 is engaged by linking the sun 2b and the ring 4b of the output planetary gearset 12. The output planetary gearset 12 is then turning as a whole and the output speed equals the ring 4b speed.


An additional gearbox 22 is added to increase the spread, allowing lower forward speeds and reverse. Since this concept has not an IVP function, a slipping clutch or a torque converter may be needed to start from standstill and to have very low driving speeds.


The transition between the three modes can simply be done by closing one of the clutches 16, 18 or brake 14 and releasing the others. This device is able to change continuously its ratio to provide the best ratio achievable for the engine in function of the objectives of consumption or power. In a manual or automatic transmission, only some predetermined and discrete ratios are available and an interruption of the power transmission is needed to shift of ratio. Generally, the power interruptions in this device only occur during gear shifting of the additional gearbox 22. Other advantages of this configuration are that a very small variator can be chosen; spread is similar to a traditional gearbox if an additional (smaller) gearbox is added and the native efficiency of the transmission is increased by using the CVP in a powersplit device, therefore letting a part of the power passing through a more efficient mechanical path. Native efficiency will be high, because the variator input ring is connected to the sun 2a, where the torque is lower, so more power is transmitted through the mechanical paths. An additional feature of this configuration is that in CVP 2 mode, powersplitting occurs two times.


Provided herein is a vehicle comprising the power transmission apparatus of any of embodiment described herein, or obvious to one of skill in the art upon reading the disclosures herein. Embodiments of the power transmission apparatus (variable transmission) described herein or that would be obvious to one of skill in the art upon reading the disclosure herein are contemplated for use in a variety of vehicle drivelines. For non-limiting example, the variable transmissions disclosed herein may be used in bicycles, mopeds, scooters, motorcycles, automobiles, electric automobiles, trucks, sport utility vehicles (SUV's), lawn mowers, tractors, harvesters, agricultural machinery, all terrain vehicles (ATV's), jet ski's, personal watercraft vehicles, airplanes, trains, helicopters, buses, forklifts, golf carts, motorships, steam powered ships, submarines, space craft, or other vehicles that employ a transmission.


While the figures and description herein are directed to ball-type variators (CVTs), alternate embodiments are contemplated another version of a variator (CVT), such as a Variable-diameter pulley (VDP) or Reeves drive, a toroidal or roller-based CVT (Extroid CVT), a Magnetic CVT or mCVT, Ratcheting CVT, Hydrostatic CVTs, Naudic Incremental CVT (iCVT), Cone CVTs, Radial roller CVT, Planetary CVT, or any other version CVT.


In some embodiments, the power transmission apparatus further comprises a traction fluid.


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.

Claims
  • 1. An apparatus for power transmission comprising: a power input shaft;a planetary gear set engaged with the power input shaft; anda ball type variator including an input ring and an output ring engaged with the gear set,wherein the apparatus is configured to split torque between a first torque path and a second torque path, wherein the ball-type variator comprises a plurality of balls in contact with the input ring and the output ring, each ball provided with a tiltable axis of rotation,wherein a speed of the output ring is continuously variable corresponding to movement of the tiltable axis of rotation, wherein the planetary gear set comprisesa set of planet gears, a sun engaged with the set of planet gears and to the input ring of the variator, a carrier engaged with the power input shaft and with the set of planet gears, and a ring gear engaged with the set of planet gears and with the output ring of the variator, andwherein the first torque path transmits rotational power passes from the power input shaft to the carrier of the planetary gear set, to the planet gears of the planetary gear set, to the sun gear of the planetary pear set, to the input ring of the variator, to the output ring of the variator, and then to the ring gear of the planetary gear set.
  • 2. The power transmission apparatus of claim 1, wherein the second torque path passes from the power input shaft to the carrier of the planetary gear set, to the planet gears of the planetary gear set, and then to the ring gear of the planetary gear set.
  • 3. The power transmission apparatus of claim 1, further comprising a gear box for transmitting an output power from the apparatus, the gear box being coupled to the planetary gear set.
  • 4. The power transmission apparatus of claim 3, wherein the gear box is coupled to the ring gear of the planetary gear set.
  • 5. The power transmission apparatus of claim 3, wherein the gear box is coupled to a differential.
  • 6. The power transmission apparatus of claim 5, wherein the gear box comprises a three speed gear box.
  • 7. The power transmission apparatus of claim 1 further comprising a traction fluid lubricant.
  • 8. A vehicle comprising the power transmission apparatus of claim 1.
  • 9. A method of transmitting power comprising: driving an input shaft;splitting torque from the input shaft between a first torque path and a second torque path; andcombining the first and second torque paths to form a single output,wherein the first and second torque paths pass through a planetary gear set and the first torque path passes through a ball type variator coupled to the planetary gear set,wherein the ball-type variator comprises a plurality of balls in contact with an input ring and an output ring, each ball provided with a tiltable axis of rotation, wherein a speed of the output ring is continuously variable corresponding to movement of the tiltable axis of rotation, andwherein splitting torque further comprises transmitting rotational power through the first torque path, wherein the first torque path corresponds to power transmission from the power input shaft to a carrier of the planetary gear set, to a set of planet gears of the planetary gear set, to a sun gear of the planetary gear set, to an input ring of the variator, to the output ring of the variator, and then to a ring gear of the planetary gear set.
  • 10. The power transmission method of claim 9, wherein splitting torque further comprises transmitting rotational power through the second torque path, wherein the second torque path corresponds to power transmission from the power input shaft to a carrier of the planetary gear set, to a set of planet gears of the planetary gear set, and then to a ring gear of the planetary gear set.
  • 11. An apparatus for power transmission comprising: a power input shaft;a planetary gear set engaged with the power input shaft; anda ball type variator including an input ring and an output ring engaged with the gear set, wherein the apparatus is configured to split torque between a first torque path and a second torque path,wherein the ball-type variator comprises a plurality of balls in contact with the input ring and the output ring, each ball provided with a tiltable axis of rotation,wherein a speed of the output ring is continuously variable corresponding to movement of the tiltable axis of rotation,wherein the planetary gear set comprises a set of planet gears, a sun engaged with the set of planet gears and to the input ring of the variator, a carrier engaged with the power input shaft and with the set of planet gears, anda ring gear engaged with the set of planet gears and with the output ring of the variator, and
RELATED APPLICATIONS

This application is a divisional application of U.S. Non-Provisional application Ser. No. 14/425,600 filed on Mar. 3, 2015 which is a United States National Phase Application of International Application No. PCT/US/2013/057868, filed on Sep. 3, 2013, which claims the benefit of U.S. Provisional Application No. 61/697,917, filed Sep. 7, 2012 and U.S. Provisional Application No. 61/779,687, filed Mar. 13, 2013, which are incorporated herein by reference.

US Referenced Citations (278)
Number Name Date Kind
1063244 Dieterich Jun 1913 A
1215969 Murray Feb 1917 A
1526140 Gruver Feb 1925 A
2019006 Ferrari Oct 1935 A
2060884 Madle Nov 1936 A
2148759 Grand Feb 1939 A
2405201 Franck Aug 1946 A
2660897 Neidhart et al. Dec 1953 A
2729118 Emslie Jan 1956 A
2931235 Hayward Apr 1960 A
3203278 General Aug 1965 A
3376633 Wesley Apr 1968 A
3407687 Hayashi Oct 1968 A
3470720 Eklund et al. Oct 1969 A
3505718 Carlstrom Apr 1970 A
3583060 Sigmans Jun 1971 A
3688600 Leonard Sep 1972 A
3765270 Lemieux Oct 1973 A
3774280 Eklund et al. Nov 1973 A
3831245 Amos Aug 1974 A
3894559 DePuy Jul 1975 A
4046988 Okuda et al. Sep 1977 A
4056988 Kubo et al. Nov 1977 A
4187709 Legate et al. Feb 1980 A
4226140 Gaasenbeek Oct 1980 A
4333358 Grattapaglia Jun 1982 A
4344336 Carriere Aug 1982 A
4360090 Wonn Nov 1982 A
4368572 Kanazawa et al. Jan 1983 A
4464952 Stubbs Aug 1984 A
4693134 Kraus Sep 1987 A
4731044 Mott Mar 1988 A
4756211 Fellows Jul 1988 A
4784017 Johnshoy Nov 1988 A
4856371 Kemper Aug 1989 A
4856374 Kreuzer Aug 1989 A
4950208 Tomlinson Aug 1990 A
4963122 Ryan Oct 1990 A
4963124 Takahashi et al. Oct 1990 A
5109962 Sato May 1992 A
5168778 Todd et al. Dec 1992 A
5217412 Indlekofer et al. Jun 1993 A
5230670 Hibi Jul 1993 A
5238460 Esaki et al. Aug 1993 A
5318486 Lutz Jun 1994 A
5390759 Gollner Feb 1995 A
5401221 Fellows et al. Mar 1995 A
5520588 Hall, III May 1996 A
5527231 Seidel et al. Jun 1996 A
5577423 Mimura Nov 1996 A
5599251 Beim et al. Feb 1997 A
5659956 Braginsky et al. Aug 1997 A
5683322 Meyerle Nov 1997 A
5726353 Matsuda et al. Mar 1998 A
5730678 Larkin Mar 1998 A
5766105 Fellows et al. Jun 1998 A
5776028 Matsuda et al. Jul 1998 A
5800303 Benford Sep 1998 A
5860888 Lee Jan 1999 A
5915801 Taga et al. Jun 1999 A
5961415 Justice et al. Oct 1999 A
5971883 Klemen Oct 1999 A
5996226 Gibbs Dec 1999 A
6009365 Takahara et al. Dec 1999 A
6036616 McCarrick et al. Mar 2000 A
6045477 Schmidt Apr 2000 A
6053839 Baldwin et al. Apr 2000 A
6059685 Hoge et al. May 2000 A
6071208 Koivunen Jun 2000 A
6080080 Bolz et al. Jun 2000 A
6083135 Baldwin et al. Jul 2000 A
6086504 Illerhaus Jul 2000 A
6089287 Welsh et al. Jul 2000 A
6095942 Yamaguchi et al. Aug 2000 A
6155951 Kuhn et al. Dec 2000 A
6217474 Ross et al. Apr 2001 B1
6251038 Ishikawa et al. Jun 2001 B1
6273838 Park Aug 2001 B1
6342026 Takagi et al. Jan 2002 B1
6358178 Wittkopp Mar 2002 B1
6371880 Kam Apr 2002 B1
6405117 Walenty et al. Jun 2002 B1
6481258 Belinky Nov 2002 B1
6554735 Kanazawa Apr 2003 B2
6558285 Sieber May 2003 B1
6585619 Henzler Jul 2003 B2
6609994 Muramoto Aug 2003 B2
6632157 Gierling et al. Oct 2003 B1
6641497 Deschamps et al. Nov 2003 B2
6645106 Goo Nov 2003 B2
6689012 Miller et al. Feb 2004 B2
6705964 Nagai et al. Mar 2004 B2
6719659 Geiberger et al. Apr 2004 B2
6723016 Sumi Apr 2004 B2
6726590 Henzler et al. Apr 2004 B2
6733412 Kumagai et al. May 2004 B2
6752696 Murai et al. Jun 2004 B2
6793603 Teraoka et al. Sep 2004 B2
6849020 Sumi Feb 2005 B2
6866606 Ooyama Mar 2005 B2
6949045 Wafzig et al. Sep 2005 B2
6979275 Hiraku et al. Dec 2005 B2
6986725 Morscheck Jan 2006 B2
7033298 Usoro et al. Apr 2006 B2
7074154 Miller Jul 2006 B2
7086981 Ali et al. Aug 2006 B2
7104917 Klemen et al. Sep 2006 B2
7128681 Sugino et al. Oct 2006 B2
7160220 Shinojima et al. Jan 2007 B2
7186199 Baxter et al. Mar 2007 B1
7217214 Morscheck May 2007 B2
7234543 Schaaf Jun 2007 B2
7288044 Gumpoltsberger Oct 2007 B2
7311634 Shim Dec 2007 B2
7335126 Tsuchiya et al. Feb 2008 B2
7347801 Guenter et al. Mar 2008 B2
7396309 Heitz et al. Jul 2008 B2
7431677 Miller et al. Oct 2008 B2
7470210 Miller et al. Dec 2008 B2
7473202 Morscheck et al. Jan 2009 B2
7485069 Jang et al. Feb 2009 B2
7497798 Kim Mar 2009 B2
7588514 McKenzie et al. Sep 2009 B2
7637838 Gumpoltsberger Dec 2009 B2
7672770 Inoue et al. Mar 2010 B2
7686729 Miller et al. Mar 2010 B2
7717815 Tenberge May 2010 B2
7727107 Miller Jun 2010 B2
7780566 Seo Aug 2010 B2
7874153 Bhem Jan 2011 B2
7878935 Lahr Feb 2011 B2
7951035 Platt May 2011 B2
7980972 Starkey et al. Jun 2011 B1
8029401 Johnson Oct 2011 B2
8052569 Tabata et al. Nov 2011 B2
8062175 Krueger et al. Nov 2011 B2
8066614 Miller et al. Nov 2011 B2
8142323 Tsuchiya et al. Mar 2012 B2
8226518 Parraga Gimeno Jul 2012 B2
8257216 Hoffman Sep 2012 B2
8257217 Hoffman Sep 2012 B2
8287414 Weber et al. Oct 2012 B2
8313404 Carter et al. Nov 2012 B2
8376903 Pohl et al. Feb 2013 B2
8382636 Shiina et al. Feb 2013 B2
8447480 Usukura May 2013 B2
8469856 Thomassy Jun 2013 B2
8545368 Davis et al. Oct 2013 B1
8594867 Heap et al. Nov 2013 B2
8622871 Hoff Jan 2014 B2
8639419 Roli et al. Jan 2014 B2
8668614 Sherrill et al. Mar 2014 B2
8678975 Koike Mar 2014 B2
8870711 Pohl et al. Oct 2014 B2
8888643 Lohr et al. Nov 2014 B2
8926468 Versteyhe et al. Jan 2015 B2
8986150 Versteyhe et al. Mar 2015 B2
9052000 Cooper Jun 2015 B2
9114799 Tsukamoto et al. Aug 2015 B2
9156463 Legner Oct 2015 B2
9228650 Schoolcraft Jan 2016 B2
9551404 Ziech et al. Jan 2017 B2
20020004438 Toukura et al. Jan 2002 A1
20020094911 Haka Jul 2002 A1
20020169048 Henzler et al. Nov 2002 A1
20030060318 Sumi Mar 2003 A1
20030181280 Elser et al. Sep 2003 A1
20030200783 Shai Oct 2003 A1
20030213125 Chiuchang Nov 2003 A1
20030216121 Yarkosky Nov 2003 A1
20030228952 Joe et al. Dec 2003 A1
20040058769 Larkin Mar 2004 A1
20040061639 Voigtlaender et al. Apr 2004 A1
20040166984 Inoue Aug 2004 A1
20040167391 Solar et al. Aug 2004 A1
20040171452 Miller et al. Sep 2004 A1
20050102082 Joe et al. May 2005 A1
20050137046 Miller et al. Jun 2005 A1
20050153810 Miller et al. Jul 2005 A1
20060094515 Szuba et al. May 2006 A1
20060234822 Morscheck et al. Oct 2006 A1
20060276294 Coffey et al. Dec 2006 A1
20070021259 Tenberge Jan 2007 A1
20070032327 Raghavan et al. Feb 2007 A1
20070042856 Greenwood Feb 2007 A1
20070072732 Klemen Mar 2007 A1
20070096556 Kokubo et al. May 2007 A1
20070270270 Miller et al. Nov 2007 A1
20070275808 Iwanaka et al. Nov 2007 A1
20080039273 Smithson et al. Feb 2008 A1
20080103002 Holmes May 2008 A1
20080121487 Miller et al. May 2008 A1
20080185201 Bishop Aug 2008 A1
20090017959 Triller Jan 2009 A1
20090048054 Tsuchiya et al. Feb 2009 A1
20090062064 Kamada et al. Mar 2009 A1
20090112424 Dahl et al. Apr 2009 A1
20090132135 Quinn, Jr. et al. May 2009 A1
20090221391 Bazyn et al. Sep 2009 A1
20090221393 Kassler Sep 2009 A1
20090286651 Tanaka et al. Nov 2009 A1
20090312137 Rohs et al. Dec 2009 A1
20100056322 Thomassy Mar 2010 A1
20100093476 Carter et al. Apr 2010 A1
20100093479 Carter et al. Apr 2010 A1
20100106386 Krasznai et al. Apr 2010 A1
20100113211 Schneider et al. May 2010 A1
20100137094 Pohl Jun 2010 A1
20100141193 Rotondo et al. Jun 2010 A1
20100244755 Kinugasa et al. Sep 2010 A1
20100267510 Nichols et al. Oct 2010 A1
20100282020 Greenwood et al. Nov 2010 A1
20100304915 Lahr Dec 2010 A1
20100310815 Mendonca Alves et al. Dec 2010 A1
20110015021 Maguire et al. Jan 2011 A1
20110034284 Pohl et al. Feb 2011 A1
20110152031 Schoolcraft Jun 2011 A1
20110165982 Hoffman et al. Jul 2011 A1
20110165985 Hoffman et al. Jul 2011 A1
20110165986 Hoffman et al. Jul 2011 A1
20110165987 Hoffman et al. Jul 2011 A1
20110230297 Shiina et al. Sep 2011 A1
20110300954 Szuba et al. Dec 2011 A1
20110319222 Ogawa et al. Dec 2011 A1
20120024991 Pilch et al. Feb 2012 A1
20120035016 Miller et al. Feb 2012 A1
20120040794 Schoolcraft Feb 2012 A1
20120122624 Hawkins, Jr. et al. May 2012 A1
20120142477 Winter Jun 2012 A1
20120165154 Wittkopp et al. Jun 2012 A1
20120231925 Shiina et al. Sep 2012 A1
20120244990 Ogawa et al. Sep 2012 A1
20120309579 Miller et al. Dec 2012 A1
20130096797 Whitney et al. Apr 2013 A1
20130130859 Lundberg et al. May 2013 A1
20130133965 Books May 2013 A1
20130184115 Urabe et al. Jul 2013 A1
20130190131 Versteyhe et al. Jul 2013 A1
20130226416 Seipold et al. Aug 2013 A1
20130281244 Vaughn Oct 2013 A1
20130303325 Carey et al. Nov 2013 A1
20130304344 Abe Nov 2013 A1
20130338888 Long et al. Dec 2013 A1
20140194242 Cooper Jul 2014 A1
20140194243 Versteyhe et al. Jul 2014 A1
20140223901 Versteyhe et al. Aug 2014 A1
20140274536 Versteyhe et al. Sep 2014 A1
20140274540 Schoolcraft Sep 2014 A1
20140274552 Frink et al. Sep 2014 A1
20140329637 Thomassy et al. Nov 2014 A1
20150024899 Phillips Jan 2015 A1
20150051801 Quinn, Jr. et al. Feb 2015 A1
20150111683 Versteyhe et al. Apr 2015 A1
20150111693 Wang et al. Apr 2015 A1
20150142281 Versteyhe et al. May 2015 A1
20150159741 Versteyhe et al. Jun 2015 A1
20150198246 Callaway et al. Jul 2015 A1
20150204429 Versteyhe et al. Jul 2015 A1
20150204430 Versteyhe et al. Jul 2015 A1
20150226294 Ziech et al. Aug 2015 A1
20150226298 Versteyhe et al. Aug 2015 A1
20150226299 Cooper et al. Aug 2015 A1
20150252881 Versteyhe Sep 2015 A1
20150354676 Versteyhe et al. Dec 2015 A1
20160033021 Cooper et al. Feb 2016 A1
20160047448 Versteyhe et al. Feb 2016 A1
20160069442 Versteyhe et al. Mar 2016 A1
20160109001 Schoolcraft Apr 2016 A1
20160116036 Schoolcraft Apr 2016 A1
20160131235 Phillips May 2016 A1
20160195173 Versteyhe et al. Jul 2016 A1
20160195177 Versteyhe et al. Jul 2016 A1
20160319731 Versteyhe et al. Nov 2016 A1
20160356366 Versteyhe et al. Dec 2016 A1
20170082049 David et al. Mar 2017 A1
20170082193 David et al. Mar 2017 A1
20170089433 Stevenson et al. Mar 2017 A1
20170089434 Waltz et al. Mar 2017 A1
Foreign Referenced Citations (73)
Number Date Country
2011224083 Oct 2011 AU
101392825 Mar 2009 CN
101479503 Jul 2009 CN
101617146 Dec 2009 CN
102297255 Dec 2011 CN
102338208 Feb 2012 CN
202165536 Mar 2012 CN
202392067 Aug 2012 CN
1237380 Mar 1967 DE
3245045 Jun 1984 DE
102005010751 Sep 2006 DE
0156936 Oct 1985 EP
0210053 Jan 1987 EP
1061288 Dec 2000 EP
1174645 Jan 2002 EP
2113056 Jul 2012 EP
796188 Mar 1936 FR
1030702 Jun 1953 FR
1472282 Mar 1967 FR
2185076 Dec 1973 FR
2280451 Feb 1976 FR
2918433 Jan 2009 FR
1127825 Sep 1968 GB
2196892 May 1988 GB
2248895 Apr 1992 GB
H09119506 May 1997 JP
2008180214 Aug 2008 JP
2009058085 Mar 2009 JP
2011153583 Aug 2011 JP
2006002457 Jan 2006 WO
2006041718 Apr 2006 WO
2006109158 Oct 2006 WO
2007046722 Apr 2007 WO
2007051827 May 2007 WO
2008101070 Aug 2008 WO
2008103543 Aug 2008 WO
2011011991 Feb 2011 WO
2012008884 Jan 2012 WO
2012177187 Dec 2012 WO
2013109723 Jul 2013 WO
2013123117 Aug 2013 WO
2014039438 Mar 2014 WO
2014039439 Mar 2014 WO
2014039440 Mar 2014 WO
2014039447 Mar 2014 WO
2014039448 Mar 2014 WO
2014039708 Mar 2014 WO
2014039713 Mar 2014 WO
2014039846 Mar 2014 WO
2014039900 Mar 2014 WO
2014039901 Mar 2014 WO
2014078583 May 2014 WO
2014124291 Aug 2014 WO
2014151889 Sep 2014 WO
2014159755 Oct 2014 WO
2014159756 Oct 2014 WO
2014165259 Oct 2014 WO
2014179717 Nov 2014 WO
2014179719 Nov 2014 WO
2014186732 Nov 2014 WO
2014197711 Dec 2014 WO
2015059601 Apr 2015 WO
2015073883 May 2015 WO
2015073887 May 2015 WO
2015073948 May 2015 WO
2015195759 Dec 2015 WO
2015200769 Dec 2015 WO
2016094254 Jun 2016 WO
2016168439 Oct 2016 WO
2016178913 Nov 2016 WO
2016182838 Nov 2016 WO
2016205639 Dec 2016 WO
2017027404 Feb 2017 WO
Non-Patent Literature Citations (3)
Entry
Fallbrook Technologies Inc. NuVinci® Technology, Feb. 26, 2013; [Retrieved from internet on Jun. 5, 2014].: URL:https://web.archive.org/web/20130226233109/http://www.fallbrooktech.com/nuvinci-technology.
Moore, C. A. et al. A Three Revolute Cobot Using CVTs in Parallel, Proceedings of IMECE, 1999, 6 pgs.
Wong. The Temple of VTEC Asia Special Focus on the Multimatic Transmission. Temple of VTEC Asia. Oct. 2000.
Related Publications (1)
Number Date Country
20170184188 A1 Jun 2017 US
Provisional Applications (2)
Number Date Country
61779687 Mar 2013 US
61697917 Sep 2012 US
Divisions (1)
Number Date Country
Parent 14425600 US
Child 15423131 US