WO2005111472A1 - Hydraulikkreis für ein toroidgetriebe - Google Patents
Hydraulikkreis für ein toroidgetriebe Download PDFInfo
- Publication number
- WO2005111472A1 WO2005111472A1 PCT/EP2005/004970 EP2005004970W WO2005111472A1 WO 2005111472 A1 WO2005111472 A1 WO 2005111472A1 EP 2005004970 W EP2005004970 W EP 2005004970W WO 2005111472 A1 WO2005111472 A1 WO 2005111472A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- control device
- clutch
- roller
- hydraulic
- Prior art date
Links
- 230000005540 biological transmission Effects 0.000 title abstract description 31
- 239000010687 lubricating oil Substances 0.000 claims description 33
- 239000003921 oil Substances 0.000 claims description 16
- 230000002706 hydrostatic effect Effects 0.000 claims description 5
- 238000001816 cooling Methods 0.000 description 11
- 230000001105 regulatory effect Effects 0.000 description 10
- 230000008878 coupling Effects 0.000 description 8
- 238000010168 coupling process Methods 0.000 description 8
- 238000005859 coupling reaction Methods 0.000 description 8
- 238000013016 damping Methods 0.000 description 7
- 230000003993 interaction Effects 0.000 description 5
- 230000001276 controlling effect Effects 0.000 description 3
- 230000001050 lubricating effect Effects 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 3
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 239000000969 carrier Substances 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/664—Friction gearings
- F16H61/6649—Friction gearings characterised by the means for controlling the torque transmitting capability of the gearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/664—Friction gearings
- F16H61/6648—Friction gearings controlling of shifting being influenced by a signal derived from the engine and the main coupling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
- F16H15/04—Gearings providing a continuous range of gear ratios
- F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
- F16H15/32—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
- F16H15/36—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
- F16H15/38—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces
- F16H2015/383—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces with two or more sets of toroid gearings arranged in parallel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
- F16H2061/0037—Generation or control of line pressure characterised by controlled fluid supply to lubrication circuits of the gearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
Definitions
- the present invention relates to a hydraulic circuit for a toroidal transmission.
- Continuously variable transmissions generally enable the internal combustion engine, which is usually connected upstream in motor vehicles, to be operated in a favorable speed range regardless of the respective speed. This improves the efficiency of the drive train, which is formed by the internal combustion engine and the continuously variable transmission. Continuously variable transmissions also offer particularly high driving comfort.
- the so-called toroidal transmission has a special meaning, especially because of its higher torque capacity compared to continuously variable belt transmission (CVTs).
- the Torotrak TM system receives special attention within the toroidal gears (see www.torotrak.com).
- This transmission does not need a starting clutch on the input side or a hydrodynamic torque converter.
- It is a full toroidal gearbox that is generally built like a countershaft gearbox.
- the variator ensures a continuous adjustment of the translation.
- the variator has a drive pulley and an output pulley, which define a toroidal ⁇ .
- three rollers are arranged distributed over the circumference, which are designed to transmit torque from the drive pulley to the driven pulley.
- the scooters are spatially adjusted within the toroid space.
- the scooters are adjusted using double-acting hydraulic cylinders.
- the actuator system required for torque support to support at least one of the disks in the axial direction is also designed hydraulically in the Torotrak system.
- two transmission ranges can be set using two clutches.
- the clutches are also actuated by hydraulic actuators.
- the torque transmission from the drive pulley to the scooter or from the scooter to the driven pulley requires a high cooling capacity, which is usually provided by lubricating oil or cooling oil. It must also be ensured that a lubricating film in the area of the contact ellipses between the rollers and the disks does not tear off.
- a hydraulic circuit for such a toroidal transmission is known from GB-A-2 369 164.
- the hydraulic circuit known from this publication has a tandem pump which pumps oil into two separate hydraulic circuits.
- One hydraulic circuit is connected to a chamber of the double-acting piston / cylinder arrangement of the respective scooter.
- the other hydraulic circuit is connected to the other chambers.
- a piston / cylinder unit is designed as a “master” for each of the hydraulic circuits. Variable throttles are formed in these. In normal operation, the oil flows through the corresponding chambers into respective proportional pressure relief valves. operated the pressure in the chambers (and consequently the force exerted by the respective roller actuators). Only in the end position range of the master of the piston / cylinder arrangements does their throttling function have an impact. The piston crown throttles the impressed volume flow by closing the outlet opening in the cylinder cover. The pistons of these piston / cylinder arrangements thus protect the actuator system against mechanical impact.
- These hydraulic stops in the end positions of the roller actuator system represent an active end position damping ("hydraulic stop"). In contrast to classic end position damping systems, this end position damping requires hydraulic power. End position damping also allows the interactions for axial pressure (disc Actuator) of the variator
- the hydraulically controlled variator is formally safe.
- Control devices for controlling the range clutches can either be connected downstream of the master piston / cylinder arrangements.
- a hydraulic-mechanical linkage can take place (for example, using a shuttle valve). This compares the pressures upstream of the proportional pressure relief valves. The higher pressure in each case serves as a source for the contact pressure of the switched range couplings.
- a second shuttle valve is provided for the hydraulic supply of a disk control device for the hydraulic pressing of at least one variator disk in the axial direction (“end load system”). This compares the pressures that of the tandem pump. The higher pressure serves as a source for the pressure on the disc.
- a lubricating oil circuit is connected to the hydraulic control circuit.
- the lubricating oil circuit requires a flow pressure to overcome the hydraulic resistances.
- the hydraulic resistances of an external cooling system and the parallel resistances of scooters, discs, bearings and wheelsets must be overcome.
- This known hydraulic circuit is robust against mechanical disturbances from the drive train. This is achieved by two separate hydraulic circuits with impressed volume flows. The mechanical-hydraulic linkage ensures safe operation. Safe emergency operation can thus be implemented.
- the implemented hydraulic concept includes hydraulic interactions at the hydraulic performance level.
- the pressure from the volume flow, which determines the roller actuator system is used directly for disc control and clutch control.
- Two pumps (tandem pump) are also required.
- a single pump is provided.
- a first main pressure is regulated in a main pressure line by means of a solenoid valve.
- the pump pressure becomes a secondary pressure in a secondary pressure line generated, by means of another solenoid valve.
- the two pressures are used to control the translation (roller actuators).
- a lubricating oil flow is derived from the pump pressure, which is partly passed through a cooler.
- the lubricating oil pressure is also regulated.
- a suitable clutch control pressure is also derived from the main pressure in the main pressure line by means of suitable solenoid valves, for actuating area clutches of the toroidal transmission.
- the axial contact pressure of the variator discs takes place via a mechanical spring arrangement.
- a hydraulic circuit for a toroidal transmission which has: a single pump, a main pressure control device which is connected to the pump, for generating a main line pressure in a main line, a scooter control device which is connected to the main line, wherein two scooter control pressures are generated in the scooter control device from the main line pressure, at least one hydraulic scooter actuator for the spatial adjustment of a scooter in a toroid space, which is set up by two disks , wherein the roller actuator is connected to the roller control device, a disk control device which is connected to the main line, a disk control pressure being generated in the disk control device from the main line pressure, and at least one hydraulic disk Actuator for the axial adjustment of at least one of the disks, the disk actuator being connected to the disk control device.
- the hydraulic systems are controlled or regulated separately from each other. This allows the individual systems and their functionality to be optimized.
- a clutch pressure control device which generates a clutch pressure in a clutch line from the main line pressure.
- a further hydraulic auxiliary system (for one or more clutches) is provided, decoupled from the other hydraulic auxiliary systems (for scooters or disks).
- the measure of deriving the clutch pressure from the main line pressure creates an economically sensible cascaded arrangement.
- a clutch control device which is connected to the clutch line, a clutch control pressure being generated in the clutch control device from the clutch pressure.
- the clutch control device is fed from the clutch line with the clutch pressure.
- a control pressure for actuating a clutch for example a range clutch or a plurality of range clutches of the toroidal transmission, is generated from this. Accordingly, it is advantageous here if at least one hydraulic clutch actuator is provided for actuating at least one area clutch, the clutch actuator being connected to the clutch control device.
- a cooler pressure control device which generates a cooler pressure in a cooler line from the clutch pressure.
- a cooler is preferably provided, which is connected to the cooler line.
- a lubricating oil pressure control device which generates a lubricating oil pressure in a lubricating oil line from the radiator pressure.
- the lubricating oil line is connected to the outlet of a cooler.
- the oil circuit connected to it can be used for both lubrication and cooling purposes and can be branched accordingly.
- the lubricating oil line is connected to the roller control device and absorbs oil displaced from the roller control device.
- the individual pump of the hydraulic circuit is a hydrostatic pump.
- the present invention creates clear advantages over the prior art.
- the individual secondary circuits for the individual functions such as roller circuit, disc circuit, clutch circuit, etc. are hydraulically decoupled from one another.
- the individual components of these circles and their functions can be better optimized. There are no hydraulic interactions.
- the pressure regulator cascade formed in total can optimally derive the hydraulic pressure that is particularly suitable for the function required in each case.
- the advantages of the prior art system according to GB 2 369 164 A as described above are retained. This applies in particular to the possibility of setting up hydraulic end position damping in the roller actuators.
- the roller actuator can also be designed classically in the manner of a double-acting piston / cylinder arrangement.
- Fig. 1 is a schematic view of a toroidal gear
- Fig. 2 is a block diagram of a hydraulic circuit according to a preferred embodiment of the invention.
- a schematically shown toroidal gear is generally designated 10.
- the toroidal transmission 10 has a transmission input shaft 12, a countershaft 14 and a transmission output shaft 16.
- a variator arrangement of the toroidal transmission 10 is shown at 20.
- the variator arrangement 20 has a main variator shaft 22 and a variator auxiliary shaft 24.
- the variator arrangement 20 further includes two variators 26A, 26B.
- Each variator 26A, 26B has a drive pulley 28A or 28B and an output pulley 30A or 30B.
- the drive pulleys 28A, 28B each enclose a toroidal space 32A, 32B with the respective driven pulleys 30A, 30B.
- a plurality of rollers 34 are arranged in the toroid spaces 32A, 32B, distributed over the circumference of the toroid space, generally three rollers 34 each.
- rollers 34 can be spatially adjusted within the toroid space 32 by means of an actuator system, not shown, as is shown schematically at 36, in order to change the translation of the variator arrangement 20. It goes without saying that all the rollers 34 of the variators 26A, 26B are adjusted in the same direction in order to be able to absorb the reaction forces that occur evenly over the circumference of the variator arrangement 20.
- a disc of a variator is pressed axially. This contact pressure is provided by a disk actuator system. As a rule, one of the two disks 28, 30 of a variator 26 is pressed on. However, both disks can also be pressed on.
- a wheel set is shown which connects the countershaft 14 in a constant manner to the variator auxiliary shaft 24, on which the drive pulleys 28A, 28B are fixed.
- the output disks 30A, 30B are fixed to the variator main shaft 22, which is connected to a summing gear 40.
- the summation gear 40 has a planetary gear set 42.
- the variator main shaft 22 is connected to the sun gear of the planetary gear set 42.
- the countershaft 14 is connected to the planet carriers of the planetary gear set 42 via a further gear set (not shown).
- the sun gear can be connected to the transmission output shaft 16 via a high-regime clutch or first range clutch 44.
- the ring gear of the planetary gear set 42 can be connected to the transmission output shaft 16 via a low-regime clutch or second range clutch 46.
- An actuator system for the area clutch 44 is shown schematically at 48.
- An actuator system for the second range clutch 46 is shown schematically at 49.
- the mode of operation of the toroidal transmission 10 is generally known and is not described in detail here for reasons of a compact representation.
- FIG. 2 An embodiment of the hydraulic circuit according to the invention is generally designated by 50 in FIG. 2.
- the hydraulic circuit 50 has a pressure control section 52, a roller section 54, a disk section 56, a clutch section 58 and a lubricating oil section 60.
- a central control device 62 for controlling the hydraulic circuit 50 is also provided.
- the control device 62 also serves as an interface to other control devices, which can be provided, for example, in a vehicle in which a toroidal transmission 10 with the hydraulic circuit 50 according to the invention is installed.
- the control device 62 emits control signals 64 which are sent to individual devices of the sections 52 to 60. This is shown in each case by an arrow pointing to the respective device to be described.
- the control device 62 also makes it possible to couple the individual sections 52 to 60 with one another in terms of control technology. Because, as will be described below, a hydraulic coupling between the individual sections 52 to 60 is generally not provided.
- the pressure control section 52 has a single hydrostatic pump 70 that provides hydrostatic oil pressure.
- the pump 70 is connected to a main line 72.
- the pressure of the main line 72 is regulated by means of a main pressure control device 74.
- the main line pressure regulated in this way is designated P L.
- the pressure control section 52 also has a clutch pressure control device 78.
- the clutch pressure control device 78 is subordinate to the main pressure control device 74 and generates a clutch pressure P LCL from the main line pressure P L , which is lower than the main line pressure P L.
- the clutch pressure P LCL is impressed on a clutch line 76.
- the pressure control section 52 also has a cooler pressure control device 82.
- the cooler pressure control device 82 is subordinate to the clutch pressure control device 78 and, from the clutch pressure P LCL, generates a cooler pressure P co that is less than P LCL .
- the cooler pressure P co is impressed on a cooler line 80.
- the pressure control section 52 has a lubricating oil pressure control device 86.
- the lubricating oil pressure regulating device 86 is subordinate to the radiator pressure regulating device 82 and generates a lubricating oil pressure P LU from the radiator pressure P co .
- the lubricating oil pressure P LU is less than the radiator pressure P co .
- the lubricating oil pressure P LU is impressed on a lubricating oil line 84.
- the lubricating oil line 84 is connected to a cooling / lubricating circuit 92 and supplies this with lubricating oil for cooling / lubricating.
- the cooling / lubrication circuit 92 includes connected the variators 26, the range couplings 44, 46, the wheel sets, etc. of the toroidal transmission 10.
- the lubricating oil line 84 is also connected to an outlet of a cooler 90, which is connected on the inlet side to the cooler line 80.
- the oil volume flow provided via the lubricating oil line 84 can be cooled via the cooler 90.
- the lubricating oil line 84 is also connected to a roller control device 100. Oil that is not required there is fed into the lubricating oil line 84 and thus used for cooling / lubrication.
- the scooter control device 100 is part of the scooter section 54.
- the scooter control device 100 is connected to the main line 72 and generates two scooter control pressures P x 'and P 2 ' for a scooter actuator 102.
- the roller actuator 102 is designed as a double-acting piston / cylinder arrangement with two oil chambers. One roller control pressure P ⁇ is applied to one chamber, the other control pressure P 2 'to the other chamber.
- the roller actuator 102 can be a master piston / cylinder arrangement.
- a hydraulic active end position damping is set up in this roller actuator 102 for both directions (“hydraulic stop”). Accordingly, a volume flow emerges from the two chambers as a rule, that is when the end positions of the roller actuator 102 are not reached , the pressures of which are indicated in FIG. 2 as P 2 and P 2 .
- a variator 26 generally has three rollers 34, which are all adjusted in the same direction Accordingly, one of the scooters is regarded as a "master roller” and the control of the other scooters is subordinate to this. This is indicated schematically by the "actuator chain” 104.
- the roller pressures P x , P 2 are monitored by a logic controller.
- control pressure measuring devices are shown, which measure the roller pressures P x and P 2 and forward the measurement signals for monitoring purposes, for example to the higher-level control device 62.
- the roller actuators 102, 104 are pressure controlled by a dynamically flowing oil flow.
- the oil flow occurring on the output side is fed into the lubricating oil line 84.
- the master roller actuator 102 can be provided with an internal bypass valve to compensate for pressure disturbances caused by impressed movements and to adjust the system damping.
- the roller actuators 102, 104 and the variator 34 formed therewith are therefore formally safe.
- the disk section 56 has a disk control device 110.
- the disk control device 110 is connected to the main line 72 and is therefore parallel to the roller control device 100.
- a disk control pressure P EL is generated in the disk control device 110 and is supplied to a disk actuator 112.
- the disk control device 110 also receives an additional pressure as an input, namely a pressure P high .
- This pressure P high is the larger of the two roller pressures P lf P 2 .
- a pressure limiting function is provided in the disk control device 110, as is indicated by a dashed line and the pressure P CE .
- the disk control pressure P EL is measured and used for control purposes, for example in the control device 62.
- the clutch section 58 has a clutch control device 114.
- the clutch control device 114 is connected to the clutch line 76 and is supplied with the clutch pressure P LCL .
- the clutch control device 114 generates a clutch control pressure P CL , which is used to control a clutch actuator 118.
- the clutch actuator 118 can also include a plurality of actuators for independently controlling the range clutches 44, 46 of the toroidal transmission 10.
- a shutoff valve 116 is connected between the clutch control device 114 and the clutch actuator 118.
- This shut-off valve 116 is a safety valve which, for example, realizes a “save function” in the event of a failure of the electronics. In this case, the area couplings 44, 46 are opened and a safe state is thus established.
- the pressure ratio between roller control pressures P, P 2 'and the disk control pressure P EL is not a rigid ratio that is predetermined by the geometry.
- the filling and closing pressures of the range couplings 44, 46 can be modulated.
- the filling and closing pressures can be switched.
- the hydraulic loss line is low.
- the roller system has a high maximum adjustment speed.
- the filling times of the area couplings are short due to the controllable filling pressure.
- Oil that is not required in the variator control is used for cooling.
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007512048A JP2007537404A (ja) | 2004-05-11 | 2005-05-07 | トロイダル変速機用の油圧回路 |
US11/598,215 US7591755B2 (en) | 2004-05-11 | 2006-11-10 | Hydraulic circuit for a toroidal transmission |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102004024031A DE102004024031A1 (de) | 2004-05-11 | 2004-05-11 | Hydraulikkreis für ein Toroidgetriebe |
DE102004024031.0 | 2004-05-11 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/598,215 Continuation US7591755B2 (en) | 2004-05-11 | 2006-11-10 | Hydraulic circuit for a toroidal transmission |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005111472A1 true WO2005111472A1 (de) | 2005-11-24 |
Family
ID=34968061
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2005/004970 WO2005111472A1 (de) | 2004-05-11 | 2005-05-07 | Hydraulikkreis für ein toroidgetriebe |
Country Status (5)
Country | Link |
---|---|
US (1) | US7591755B2 (de) |
JP (1) | JP2007537404A (de) |
KR (1) | KR20070012617A (de) |
DE (1) | DE102004024031A1 (de) |
WO (1) | WO2005111472A1 (de) |
Cited By (33)
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US7166052B2 (en) * | 2003-08-11 | 2007-01-23 | Fallbrook Technologies Inc. | Continuously variable planetary gear set |
US7882762B2 (en) | 2006-01-30 | 2011-02-08 | Fallbrook Technologies Inc. | System for manipulating a continuously variable transmission |
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Also Published As
Publication number | Publication date |
---|---|
US20070167274A1 (en) | 2007-07-19 |
US7591755B2 (en) | 2009-09-22 |
KR20070012617A (ko) | 2007-01-26 |
JP2007537404A (ja) | 2007-12-20 |
DE102004024031A1 (de) | 2005-12-08 |
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