WO2014025171A1 - 변속 장치 - Google Patents
변속 장치 Download PDFInfo
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- WO2014025171A1 WO2014025171A1 PCT/KR2013/007030 KR2013007030W WO2014025171A1 WO 2014025171 A1 WO2014025171 A1 WO 2014025171A1 KR 2013007030 W KR2013007030 W KR 2013007030W WO 2014025171 A1 WO2014025171 A1 WO 2014025171A1
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- gear
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- input shaft
- transmission
- coupled
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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
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
- F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
- F16H2200/2025—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 5 connections
Definitions
- the present invention relates to a transmission, and more particularly to a transmission that automatically shifts without a clutch.
- the transmission is a device that transmits a rotation generated from a power source such as an engine to a driven body such as a wheel of a vehicle.
- a power source such as an engine
- a driven body such as a wheel of a vehicle.
- all the transmissions are shifted according to a predetermined gear ratio, and when shifting, cumbersome clutch operation is required for separation and replacement of gears.
- One object of the present invention is to provide a transmission that is automatically shifted without detachment and replacement of gears.
- the input shaft provided to receive and rotate the rotational force;
- a turbine that rotates by converting a torque of the input shaft;
- An input carrier coupled to the turbine and installed to revolve the input shaft;
- First and second shift carriers coupled to the input ring gear and revolving the input shaft;
- a first unidirectional bearing fixedly installed at an outer side thereof and provided at the inner side to be rotatable only in one direction;
- a first transmission gear coupled to the inside of the first unidirectional bearing;
- a second unidirectional bearing having an inner side coupled to the input shaft such that an outer side thereof is rotatable only below the input rotational speed;
- a second transmission gear coupled to the outside of the second unidirectional bearing;
- the idle and the rotation of the planetary gear cancel each other so that the input carrier is kept stationary, and the When the rotation speed is greater than or equal to the first threshold value and less than the second threshold value, the first unidirectional bearing acts as a rotating load so that rotational force is transmitted to the output shaft so that the output shaft rotates at a first speed ratio with respect to the input rotation speed.
- the second unidirectional bearing acts as a rotating load so that the rotational force is transmitted to the output shaft so that the output shaft becomes the output shaft.
- the second rotation speed may be larger than the first speed ratio with respect to the input rotation speed.
- the planetary gear may revolve so as to cancel its rotation so that the input ring gear can be kept stationary.
- the input shaft gear, the planetary gear and the input ring gear may be provided with a ratio of the number of gear teeth of 1: 1: 3, and the first threshold value may be 0.25.
- the first differential gear When the turbine rotational speed with respect to the rotational speed of the input shaft is greater than or equal to a first threshold value and less than or equal to a second threshold value, the first differential gear may be configured according to the rotational load generated when the first unidirectional bearing enters a stationary state.
- the output ring gear can be rotated via a second differential gear.
- the second unidirectional bearing causes the rotational load to be generated as the rotational speed reaches the input rotational speed.
- a second differential gear can rotate the output ring gear.
- the first differential gear, the second differential gear and the first transmission gear are provided with a ratio of gear teeth 7: 7: 13, and the second differential gear and the second transmission gear have a ratio of gear teeth 1
- the second threshold value is 0.5125 and the third threshold value is 1.
- the first shift carrier is installed to revolve the first shaft; A first transmission gear installed to be rotatable only in one direction; A second transmission gear installed to be capable of rotating only below a predetermined rotation speed; A first differential gear installed to insert the first shift carrier and engaged with the first shift gear; A second differential gear installed to insert the second shift carrier and engaged with the first differential gear and the second shift gear; And an output ring gear to which the second differential gear is fastened therein may be provided.
- the transmission device may further include a first unidirectional bearing having one side fixed and the other side coupled to the first transmission gear.
- the transmission device includes an input shaft installed to rotate along the first axis; And a second unidirectional bearing having one side coupled to the input shaft and the other side coupled to the second transmission gear, wherein the predetermined rotational speed may be the rotational speed of the input shaft.
- the transmission device includes an input shaft installed to rotate along the first axis; An input shaft gear formed on the input shaft; A turbine that rotates by converting a torque of the input shaft; An input carrier coupled to the turbine and installed to revolve the input shaft; A planetary gear installed to insert the input carrier and engaged with the input shaft gear; And an input ring gear to which the planetary gear is fastened therein, wherein the first shift carrier is coupled to the input ring gear and installed to revolve the input shaft.
- the shift may be automatically made according to the number of revolutions converted in the torque converter.
- FIG. 1 is a block diagram of a transmission apparatus according to an embodiment of the present invention.
- FIG. 2 is a cross-sectional view of the transmission of FIG. 1.
- FIG. 3 is a perspective view of the input unit of FIG. 2.
- FIG. 4 is a cross-sectional view of the torque converter unit of FIG. 2.
- FIG. 5 is a cross-sectional view of the torque transmission unit of FIG. 2.
- FIG. 6 is a perspective view of the torque transmission unit of FIG. 5.
- FIG. 7 is a cross-sectional view of the transmission part of FIG. 2.
- FIG. 8A is an exploded perspective view of a portion of the transmission part of FIG. 7.
- FIG. 8B is a cross-sectional view of the transmission part of FIG. 7.
- FIG. 9 is a view illustrating a fastening state of the first differential gear of FIG. 8.
- FIG. 10 is a view illustrating a fastening state of the second differential gear of FIG. 8.
- FIG. 11 is a table illustrating an example of the number of gears of the transmission device of FIG. 2.
- FIG. 12 is a table relating to a shift stage in a shift method using the shift device of FIG. 11.
- FIG. 13 is a graph illustrating the rotation speeds of the first shift gear and the second shift gear according to the shifting step of FIG. 12.
- FIG. 14 is a graph illustrating a rotation speed of an output shaft according to the shifting step of FIG. 12.
- 15 is a diagram relating to a transmission order of rotational force in the neutral state of FIG. 12.
- FIG. 16 is a table of rotation directions of gears in the neutral state of FIG. 12.
- 17 is a diagram relating to a transmission order of rotational force in the low speed state of FIG. 12.
- FIG. 19 is a diagram related to a transmission order of rotational force in the high speed state of FIG. 12.
- 20 is a table relating to a rotation direction of gears in the high speed state of FIG. 12.
- the transmission device 1000 shifts and outputs the rotation when it is input. Specifically, the transmission device 1000 converts an input rotational force, that is, a torque by applying a torque converter, and automatically shifts the gears without using a clutch by using a planetary gear and a differential gear. Output
- FIG. 1 is a block diagram of a transmission apparatus 1000 according to an exemplary embodiment of the present invention
- FIG. 2 is a cross-sectional view of the transmission apparatus 1000 of FIG. 1.
- the transmission apparatus 1000 may include an input unit 1100, a torque converter 1200, a torque transmission unit 1300, a transmission unit 1400, and an output unit 1500.
- the rotational force is input to the input unit 1100, and the torque converter 1200 converts the torque of the input rotational force.
- the torque transmission unit 1300 transmits the rotational force of the input unit 1100 and the rotational force of the torque converter unit 1200 to the transmission unit 1400 using a planetary gear structure.
- the transmission unit 1400 shifts the rotational force transmitted using the differential gear structure and outputs the output to the output unit 1500.
- the input unit 1100 receives a rotation force from the outside.
- FIG. 3 is a perspective view of the input unit 1100 of FIG. 2.
- the input unit 1100 may include an input shaft 1110, an impeller connecting member 1120, an input shaft gear 1130, and a bearing connecting member 1140.
- the input shaft 1110 is provided in the form of a rod having a circular cross section.
- the input shaft 1110 may receive a rotational force from the outside and rotate accordingly.
- the rotation speed of the input unit 1100 will be referred to as an input rotation speed.
- the impeller connecting member 1120, the input shaft gear 1130, and the bearing connecting member 1140 may be sequentially formed on the input shaft 1110.
- the impeller connecting member 1120 connects the input shaft 1110 and the impeller 1220.
- the impeller connecting member 1120 may be provided in a disc shape around the input shaft 1110 such that the shaft or plate extending from the impeller 1220 or the impeller 1220 is engaged. Accordingly, the rotational force input to the input shaft 1110 may be transmitted to the torque converter unit 1200.
- the input shaft gear 1130 may be provided in the form of a sun gear formed on the input shaft 1110.
- the input shaft gear 1130 may be engaged with the planetary gear 1330 of the torque transmission unit 1300, thereby transmitting the rotational force input to the input shaft 1110 to the torque transmission unit 1300.
- the bearing connecting member 1140 may be formed in a circular ring shape on the input shaft 1110.
- the outer circumferential surface of the bearing connecting member 1140 is engaged with the inner bearing of the second bearing 1431. Accordingly, the inner bearing of the second bearing 1431 may rotate at an input rotation speed.
- the torque converter 1200 converts torque of the rotational force transmitted from the input unit 1100.
- FIG. 4 is a cross-sectional view of the torque converter 1200 of FIG. 2.
- the torque converter unit 1200 includes a housing 1210, an impeller 1220, a turbine 1230, and a turbine shaft 1240.
- Housing 1210 houses impeller 1220, turbine 1230, and turbine shaft 1240 therein.
- the housing 1210 may be fixed to the outside to maintain a stop state regardless of the rotation of the input shaft 1110.
- the impeller 1220 is connected to the impeller connecting member 1120 to rotate integrally with the input shaft 1110.
- the impeller 1220 may be provided in a wheel shape having a plurality of wings provided to be rotatable about the input shaft 1110.
- the turbine 1230 may be provided in a wheel shape having a plurality of wings disposed to face the impeller 1220.
- the turbine 1230 may convert the torque of the rotational force of the impeller 1220.
- a fluid may be provided between the impeller 1220 and the turbine 1230 inside the housing 1210.
- kinetic energy is transferred to the fluid, which in turn causes the turbine 1230 to rotate.
- the torque may be converted while the impeller 1220 rotates the turbine 1230 through the fluid.
- the rotation speed of the converted turbine 1230 is referred to as turbine rotation speed.
- a stator (not shown) may be additionally disposed between the impeller 1220 and the turbine 1230 in the torque converter 1200.
- the stator (not shown) may increase the efficiency with which the torque is converted.
- the turbine shaft 1240 has one end extending from the turbine 1230 and the other end coupled to the input carrier 1310. Accordingly, the turbine shaft 1240 may rotate together with the turbine 1230 to transmit the rotational force of the turbine 1230 to the input carrier 1310.
- the torque transmission unit 1300 receives the rotational force from the input unit 1100 and the torque converter 1200 and transfers the rotational force to the transmission unit 1400.
- FIG. 5 is a cross-sectional view of the torque transmission unit 1300 of FIG. 2, and FIG. 6 is a perspective view of the torque transmission unit 1300 of FIG. 5.
- the torque transmission unit 1300 may include an input carrier 1310, a planetary gear 1330, an input ring gear 1320, and a transmission shaft 1340.
- the input carrier 1310 is provided in the form of a shaft revolved about the input shaft 1110.
- the input carrier 1310 may be coupled to the turbine shaft 1240 to rotate with the turbine 1230 and the turbine shaft 1240 to orbit the input shaft 1110.
- the planetary gear 1330 is provided as a hollow gear that is inserted into the input carrier 1310. Accordingly, the planetary gear 1330 may revolve the input shaft 1110 together with the input carrier 1310.
- one side of the planetary gear 1330 is fastened to the input shaft gear 1130. Accordingly, the planetary gear 1330 may rotate by receiving rotational force from the input shaft gear 1130.
- the other side of the planetary gear 1330 is coupled to the input ring gear 1320.
- the planetary gear 1330 rotates according to the input shaft gear 1130 which revolves with the input carrier 1310.
- the rotational force is applied to the input ring gear 1320 according to the combination of the revolution and the rotation. I can deliver it.
- the input ring gear 1320 is provided in the form of a ring gear to which the planetary gear 1330 is fastened therein.
- the input ring gear 1320 may rotate by receiving rotational force from the planetary gear 1330 according to a combination of revolution and rotation of the planetary gear 1330.
- One end of the transmission shaft 1340 extends from the input ring gear 1320, and the other end is coupled to the shift carrier 1410. Accordingly, the transmission shaft 1340 transmits the rotational force of the input ring gear 1320 to the transmission carrier 1410, whereby the input ring gear 1320, the transmission shaft 1340, and the transmission carrier 1410 rotate integrally. can do.
- the transmission unit 1400 shifts the rotational force transmitted from the torque transmission unit 1300 and outputs the output to the output unit 1500.
- FIG. 7 is a cross-sectional view of the shifting unit 1400 of FIG. 2
- FIG. 8A is a partially exploded perspective view of the shifting unit of FIG. 7
- FIG. 8B is a cross-sectional view of the shifting unit of FIG. 7.
- FIG. 9 is a view illustrating a coupling state between the first differential gear 1440 and the first transmission 1420 of FIG. 7,
- FIG. 10 is an output of the second differential gear 1450 and the output unit 1500 of FIG. 8. It is a figure which shows the fastening state between the ring gear 1510.
- the transmission unit 1400 may include a shift carrier 1410, a first transmission 1420, a second transmission 1430, a first differential gear 1440, and a second differential gear 1450. It includes.
- the shift carrier 1410 is provided to be rotatable on the input shaft 1110.
- the shift carrier 1410 may be coupled to the transmission shaft 1340 to rotate with the input ring gear 1320 and the transmission shaft 1340 to orbit the input shaft 1110.
- the shift carrier 1410 includes a first fixing pin 1412 and a second fixing pin so that the first differential gear 1440 and the second differential gear 1450 rotate and rotate about the input shaft 1110 at the same time. 1414 is installed. The shift carrier 1410 is engaged with a flange 1342 formed outwardly at the rear end of the transmission shaft 1340.
- the first differential gear 1440 is composed of a front end portion 1440a and a rear end portion 1440b, the first shift gear 1423 is fastened to the front end portion 1440a, and the second differential gear is attached to the rear end portion 1440b.
- 1450 may be fastened.
- the second differential gear 1450 is composed of a front end 1450a and a rear end 1450b, the first differential gear 1440 is fastened to the front end 1450a, and the second speed change is performed at the rear end 1450b.
- the gear 1433 and the output ring gear 1510 may be connected.
- the first differential gear 1440 and the second differential gear 1450 revolve around the input shaft 1110 by the shift carrier 1410 and are fastened to each other. Accordingly, the shift is performed by being constrained by either the first transmission 1420 or the second transmission 1430, and the rotational force transmitted to the output ring gear 1510 may be transmitted.
- the shifting process will be clearer in the shifting method described below.
- a first differential gear 1440 and a second differential gear 1450 are provided in pairs, respectively, and the first differential gear 1440 and the second differential gear 1450 are provided to transmit stable torque.
- the input shaft 1110 may be provided to be symmetrical to each other.
- the shift carriers 1410 may rotate at the same rotational speed.
- the first differential gear 1440 and the second differential gear 1450 may be fastened to each other.
- a first transmission 1420 is connected to the first differential gear 1440
- a second transmission gear 1433 is connected to the second differential gear 1450.
- the second differential gear 1450 is also connected to the output ring gear 1510.
- the first transmission 1420 includes a first bearing 1421, a first shift shaft 1422, and a first shift gear 1423.
- the first bearing 1421 is a unidirectional bearing centered on the input shaft 1110 and has an inner bearing and an outer bearing.
- the outer bearing is coupled to the housing 1210 and the inner bearing is coupled to the first shift shaft 1422.
- One end of the first shift shaft 1422 is coupled to the inner bearing, and the other end of the first shift shaft 1422 is provided.
- the first shift gear 1423 is engaged with the first differential gear 1440.
- the inner and outer bearings can rotate freely without load when rotational force is applied in one direction, while the inner and outer bearings can't rotate due to the opposite rotational force. This can act as a rotating load.
- a direction in which idling is possible is referred to as a free direction, and an opposite direction is referred to as a load direction.
- the outer bearing since the outer bearing is coupled to the fixed housing 1210, the outer bearing remains fixed, and the inner bearing is coupled to the first shift shaft 1422 so that the first shift shaft ( 1422).
- the inner bearing rotates in the free direction with respect to the outer bearing, rotation is possible without a load, and when rotation force is applied in the load direction, rotation of the first bearing 1421 is impossible, so that the inner bearing, the first shift shaft All of the 1422 will remain stationary.
- the second transmission 1430 includes a second bearing 1431, a second shift shaft 1432, and a second shift gear 1433.
- the second bearing 1431 is provided as a unidirectional bearing centering on the input shaft 1110, similar to the first bearing 1421, and has an inner bearing and an outer bearing.
- the inner bearing is coupled to the bearing connecting member 1140 and the outer bearing is coupled to the second shift shaft 1432.
- One end of the second shift shaft 1432 is coupled to the outer bearing, and the other end of the second shift shaft 1432 is provided.
- the second transmission gear 1433 is engaged with the second differential gear 1450.
- the second bearing 1431 since the inner bearing is coupled to the bearing connecting member 1140 formed on the input shaft 1110, the inner bearing rotates together with the input shaft 1110 at the input rotational speed, and the outer bearing has the second bearing. Since it is coupled to the shift shaft 1432, the motor rotates together with the second shift shaft 1433.
- the inner bearing rotates at the input rotational speed
- the outer bearing rotates at or below the rotational speed or in the opposite direction
- the second bearing 1431 is rotated in the free direction, which enables rotation without load, and the outer bearing.
- the rotation of the second bearing 1431 is impossible, so that the outer bearing and the second transmission shaft 1432 both maintain the rotation state at the input rotation speed.
- the second bearing 1431 when the rotational force in the free direction or the load direction is applied to the second bearing 1431 from the second differential gear 1450 even if a rotational force equal to or less than the input rotational speed is applied, the second bearing 1431 is idling to the second differential. If a load is not applied to the gear 1450 and an input rotation speed is applied to the second bearing 1431 from the second differential gear 1450 in the load direction, the second bearing 1431 and the second shift shaft Both the 1143 and the second transmission gears 1433 are fixed at the input rotational speed and rotate to apply a load to the second differential gear 1450.
- the output unit 1500 includes an output ring gear 1510 and an output shaft 1520.
- the output ring gear 1510 is provided in the form of a ring gear about the input shaft 1110.
- the second differential gear 1450 is fastened to the inside of the output ring gear 1510.
- the output ring gear 1510 receives rotational force from the second differential gear 1450.
- One end of the output shaft 1520 extends from the output ring gear 1510 and is bent at one point to extend along the direction of the input shaft 1110 in the form of a shaft.
- the output shaft 1520 may rotate integrally with the output ring gear 1510 to transmit rotational force to the outside.
- the speed change method will be described here based on the above-described speed change apparatus 1000 having the number of gears in FIG.
- the number of gears of FIG. 11 is a value determined arbitrarily and is not limited to the transmission apparatus 1000 or the shifting method.
- the number of gears of the transmission apparatus 1000 may be set differently from the numerical value of FIG. 11, and in this case, the timing at which the neutral, low speed, and high speed are shifted in the shift method may be changed. That is, the number of teeth of the gear in the transmission apparatus 1000 may be appropriately added or reduced in consideration of a desired speed ratio or shift timing.
- the transmission device 1000 may receive a rotational force from the outside and shift the output to output the rotational force.
- the transmission apparatus 1000 may perform a shift according to a neutral state, a low speed state, and a high speed state.
- FIG. 11 is a table illustrating an example of the number of gears of the transmission device 1000 of FIG. 2.
- FIG. 12 is a table illustrating a shifting step in a shift method using the transmission device 1000 of FIG. 11, and FIG. Is a graph of the rotation speed of the first shift gear 1423 and the second transmission gear 1433 according to the shift step of FIG. 14, and FIG. 14 is a graph of the rotation speed of the output shaft 1520 according to the shift step of FIG. 12. .
- the number of gear teeth is 15T for the input shaft gear 1130, 15T for the planetary gear 1330, 45T for the input ring gear 1320, and the front end 1440a and the rear end of the first differential gear 1440.
- 1440b is 14T
- the front end 1450a of the second differential gear 1450 is 14T
- the rear end 1450b is 18T
- the output ring gear 1510 is 54T
- the first transmission gear 1423 is 26T
- Two shift gears 1433 may be provided to have 18T.
- the torque transmission unit 1300 may input the input ring gear. Since the rotational force is not transmitted to 1320, the output shaft 1520 is in a neutral state in which it does not rotate.
- the torque transmission unit 1300 transmits the rotational force to the first differential gear 1440 through the input ring gear 1320 and at the same time the first bearing 1421 moves in the load direction.
- the rotational force is applied to restrain the rotation of the first transmission gear 1423.
- the first differential gear 1440 transmits the rotational force to the second differential gear 1450 while rotating and rotating according to the rotational force of the input ring gear 1320 and the restraint of the first transmission gear 1423, and the second differential.
- the gear 1450 rotates the output ring gear 1510 to output a rotational force to the output shaft 1520.
- the second bearing 1431 is idle.
- the torque transmission unit 1300 transmits the rotational force to the first differential gear 1440 through the input ring gear 1320, and the second bearing 1431 moves in the load direction.
- the rotational force is applied to restrain the rotation of the second transmission gear 1433.
- the second differential gear 1450 rotates and rotates according to the rotational force transmitted from the input ring gear 1320 and the restraint of the second transmission gear 1333 via the first differential gear 1440, and output ring gear 1510. Rotate to output a rotation force to the output shaft 1520.
- the first bearing 1421 is idle.
- the turbine speed reaches 1 equal to the input speed
- the input shaft 1110, the turbine 1230, the first transmission gear 1423, the second transmission gear 1333, and the output shaft 1520 are all input.
- the speed ratio reaches 1 by rotating at the same speed as the speed.
- the input rotational speed is +1, and other rotational speeds are referred to as a ratio thereof.
- the sign "+” means rotation in the same direction as the input rotation speed
- "-" means rotation in a direction opposite to the input rotation speed.
- -0.5 it means to rotate at a speed of 1/2 of the input rotation speed in the direction opposite to the input rotation speed.
- FIG. 15 is a diagram relating to a transmission order of rotational force in the neutral state of FIG. 12, and FIG. 16 is a table of rotation directions of gears in the neutral state of FIG. 12.
- the input shaft 1110 When a rotational force is input to the input shaft 1110, the input shaft 1110 rotates at an input rotation speed of +1.
- the impeller connecting member 1120 and the impeller 1220 rotate integrally with the input shaft 1110 at +1.
- the turbine 1230 is rotated by the impeller 1220.
- the turbine shaft 1240 and the input carrier 1310 are connected to the turbine shaft 1240 and rotate integrally with the turbine 1230.
- the planetary gear 1330 is inserted into the input carrier 1310 and rotates integrally with the input carrier 1310 and is engaged with the input shaft gear 1130 to rotate by receiving rotational force from the input shaft gear 1130. At this time, since the planetary gear 1330 is fastened to the inside of the input ring gear 1320, the planetary gear 1330 receives the rotational force received from the input carrier 1310 and the input shaft gear 1130 as a result. To pass.
- the input ring gear 1320 since the input ring gear 1320 is connected to the shift carrier 1410 of the transmission unit 1400, the input ring gear 1320 has a predetermined rotational load, and thus, when the turbine rotation speed with respect to the input rotation speed is less than the first threshold value, the input ring gear ( The input ring gear 1320 may not rotate because the rotational load of 1320 is greater. This is because the turbine 1230 is not in a physically engaged state with the impeller 1220 and is in a relationship in which rotational force is transmitted through the fluid, so that the idle of the input carrier 1310 connected to the turbine 1230 is below the first threshold value. This is because it generates little load.
- the turbine rotational speed reaches the first threshold value of +0.25.
- the rotation of the planetary gear 1330 and the revolution of the planetary gear 1330 cancel each other so that rotation force is not transmitted to the input ring gear 1320.
- the turbine rotational speed is 0.25
- the rotation speed of the planetary gear 1330 itself is four times the revolution speed
- the rotation of the planetary gear 1330 seen from the outside is canceled by one revolution when viewed from the outside.
- the number of revolutions is three times the number of revolutions. In this case, since the number of gears of the input ring gear 1320 is three times the number of gears of the planetary gear 1330 and the input shaft gear 1130, as a result, the input ring gear 1320 may maintain a stopped state.
- FIG. 17 is a diagram relating to a transmission order of rotational force in the low speed state of FIG. 12, and FIG. 18 is a table relating to the rotation direction of the gears in the low speed state of FIG. 12.
- the rotation of the planetary gear 1330 is performed when the turbine speed is +0.25.
- the idle ring cancels each other so that the input ring gear 1320 does not rotate, where the turbine rotational speed increases when the number of gears of the input ring gear 1320 engaged with the revolution enters the ring gear 1320.
- the rotation of the input ring gear 1320 may be started to be greater than the number of gears.
- the first differential gear 1440 is connected to the first transmission gear 1423 of the first transmission 1420.
- the first transmission gear 1423 is connected to the inner bearing of the first bearing 1421 via the first transmission shaft 1422.
- the first bearing 1421 is connected to the housing 1210 whose outer bearing is stationary, and generates a load when the inner bearing of the first bearing 1421 is about to rotate by the shift carrier 1410. . Accordingly, the inner bearing of the first bearing 1421 has a stationary state, and the load is transmitted to the first differential gear 1440 via the first transmission gear 1423.
- the first differential gear 1440 rotates by the shift carrier 1410 and simultaneously rotates so as not to rotate the first transmission 1420.
- the second differential gear 1450 is installed in the shift carrier 1410 and is coupled to the first differential gear 1440 and the output ring gear 1510.
- the second differential gear 1450 may rotate by the first differential gear 1440 while revolving by the shift carrier 1410. Accordingly, the second differential gear 1450 may transmit rotational force to the output ring gear 1510.
- the transmission unit 1400 transmits the rotational force to the output unit 1500 according to a constraint condition in which the first transmission 1420 maintains the stationary state.
- the output ring gear 1510 rotates when the turbine ring speed reaches +0.5125 when the turbine ring speed starts to rotate at +0.25.
- the number reaches +0.1333.
- the rotation speed of the first transmission 1420 is maintained at zero during this time.
- a second transmission 1430 is held in the second differential gear 1450.
- the second transmission 1430 has its rotation speed reaching 0 at turbine speed +0.25 and +1 at turbine speed +0.5125.
- FIG. 19 is a diagram relating to a transmission order of rotational force in the high speed state of FIG. 11, and FIG. 20 is a table relating to a rotation direction of gears in the high speed state of FIG. 12.
- the second transmission 1430 coupled to the second differential gear 1450 does not generate a load. This is because the second transmission 1430 rotates freely until the outer bearing reaches +1 since the bearing connecting member 1140 of the input shaft 1110 is coupled to the inner bearing.
- the number of gears of the first differential gear 1440 and the first shift gear 1423 is 14:26, while the number of gears of the second differential gear 1450 and the second shift gear 1433 is 14. Since 18 is 18, when the turbine speed increases from the time when the second transmission gear 1433 generates a load, the first transmission gear 1423 decreases the rotation speed so as not to generate a load. That is, the first differential gear receives force only from the input ring gear 1320 and transmits it to the second differential gear 1450.
- the second differential gear 1450 rotates by the first differential gear 1440 in a state where the rotation speed of the second shift gear 1433 is fixed at +1, and rotates by the shift carrier 1410 while output ring gear is rotated. 1510 may be rotated.
- the rotation speed of the second transmission 1430 is fixed to +1 until the turbine rotational speed reaches +1, and reaches +1.
- the output ring gear 1510 will rotate from +0.1333 to +1 revolutions.
- the transmission apparatus 1000 may selectively include all or a part of the above-described components.
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Claims (11)
- 회전력을 입력받아 자전하도록 제공되는 입력 축;상기 입력 축에 형성되는 입력 축 기어;상기 입력 축의 토크를 변환하여 회전하는 터빈;상기 터빈에 결합되고, 상기 입력 축을 공전하도록 설치되는 입력 캐리어;상기 입력 축 기어와 체결되고, 상기 입력 캐리어가 삽입되도록 설치되는 유성 기어;내부에 상기 유성 기어가 체결되는 입력 링 기어;상기 입력 링 기어에 결합되고, 상기 입력 축을 공전하도록 제1 및 제2 변속 캐리어;외측이 고정 설치되어 내측은 단방향으로만 회전 가능하도록 제공되는 제1 단방향 베어링;상기 제1 단방향 베어링의 내측에 결합되는 제1 변속 기어;상기 제1 변속 기어와 체결되고, 상기 제1 변속 캐리어가 삽입되도록 설치되는 제1 차동 기어;내측이 상기 입력 축에 결합되어 외측은 상기 입력 회전수 이하로만 회전 가능하도록 제공되는 제2 단방향 베어링;상기 제2 단방향 베어링의 외측에 결합되는 제2 변속 기어;상기 제2 변속 기어 및 상기 제1 차동 기어에 체결되고, 상기 제2 변속 캐리어에 삽입되도록 설치되는 제2 차동 기어;내부에 상기 제2 차동 기어가 체결되는 출력 링 기어; 및상기 출력 링 기어에 결합되는 출력 축;을 포함하는변속 장치.
- 제1 항에 있어서,상기 입력 축의 회전수에 대한 상기 터빈의 회전수가 제1 임계값 이하인 경우, 상기 유성 기어의 공전과 자전이 서로 상쇄되어 상기 입력 캐리어가 정지 상태로 유지되고,상기 입력 축의 회전수에 대한 상기 터빈의 회전수가 상기 제1 임계값 이상 제2 임계값 이하인 경우, 상기 제1 단방향 베어링이 회전 부하로 작용하여 상기 출력 축으로 회전력이 전달되어 상기 출력 축이 상기 입력 회전수에 대하여 제1 변속비로 회전하고,상기 입력 축의 회전수에 대한 상기 터빈의 회전수가 상기 제2 임계값 이상 제3 임계값 이하인 경우, 상기 제2 단방향 베어링이 회전 부하로 작용하여 상기 출력 축으로 회전력이 전달되어 상기 출력 축이 상기 입력 회전수에 대하여 상기 제1 변속비보다 큰 제2 변속비로 회전하는변속 장치.
- 제1 항에 있어서,상기 입력 축의 회전수에 대한 상기 터빈의 회전수가 제1 임계값 이하인 경우에는, 상기 유성 기어가 그 자전을 상쇄하도록 공전하여 상기 입력 링 기어가 정지 상태로 유지되는변속 장치.
- 제3 항에 있어서,상기 입력 축 기어, 상기 유성 기어 및 상기 입력 링 기어는 그 기어 잇수의 비가 1:1:3으로 제공되고,상기 제1 임계값은, 0.25인변속 장치.
- 제1 항에 있어서,상기 입력 축의 회전수에 대한 상기 터빈의 회전수가 제1 임계값 이상 제2 임계값 이하인 경우에는, 상기 제1 단방향 베어링이 정지 상태로 진입함에 따라 발생시키는 회전 부하에 따라 상기 제1 차동 기어가 상기 제2 차동 기어를 통해 상기 출력 링 기어를 회전시키는변속 장치.
- 제5 항에 있어서,상기 입력 축의 회전수에 대한 상기 터빈의 회전수가 상기 제2 임계값 이상 제3 임계값 이하 경우에는, 상기 제2 단방향 베어링이 그 회전수가 상기 입력 회전수에 도달함에 따라 발생시키는 회전 부하에 따라 상기 제2 차동 기어가 상기 출력 링 기어를 회전시키는변속 장치.
- 제6 항에 있어서,상기 제1 차동 기어, 상기 제2 차동 기어 및 상기 제1 변속 기어는 그 기어 잇수의 비가 7:7:13으로 제공되고,상기 제2 차동 기어 및 상기 제2 변속 기어는 그 기어 잇수의 비가 1:1로 제공되고,상기 제2 임계값은, 0.5125이고,상기 제3 임계값은, 1인변속 장치.
- 제1 축을 공전하도록 설치되는 제1 변속 캐리어;단방향으로만 자전 가능하도록 설치되는 제1 변속 기어;미리 정해진 회전수 이하로만 자전 가능하도록 설치되는 제2 변속 기어;상기 제1 변속 캐리어가 삽입되도록 설치되고, 상기 제1 변속 기어와 체결되는 제1 차동 기어;상기 제2 변속 캐리어가 삽입되도록 설치되고, 상기 제1 차동 기어 및 상기 제2 변속 기어와 체결되는 제2 차동 기어; 및내부에 상기 제2 차동 기어가 체결되는 출력 링 기어;를 포함하는변속 장치.
- 제8 항에 있어서,일측이 고정 설치되고, 타측이 상기 제1 변속 기어와 결합되는 제1 단방향 베어링;을 더 포함하는변속 장치.
- 제8 항에 있어서,상기 제1 축을 따라 자전하도록 설치되는 입력 축; 및일측이 상기 입력 축에 결합되고, 타측이 상기 제2 변속 기어와 결합되는 제2 단방향 베어링;을 더 포함하고,상기 미리 정해진 회전수는, 상기 입력 축의 회전수인변속 장치.
- 제8 항에 있어서,상기 제1 축을 따라 자전하도록 설치되는 입력 축;상기 입력 축에 형성되는 입력 축 기어;상기 입력 축의 토크를 변환하여 회전하는 터빈;상기 터빈에 결합되고, 상기 입력 축을 공전하도록 설치되는 입력 캐리어;상기 입력 캐리어가 삽입되도록 설치되고, 상기 입력 축 기어와 체결되는 유성 기어; 및내부에 상기 유성 기어가 체결되는 입력 링 기어;를 더 포함하고,상기 제1 변속 캐리어는, 상기 입력 링 기어에 결합되고, 상기 입력 축을 공전하도록 설치되는변속 장치.
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KR10-2012-0086430 | 2012-08-07 | ||
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KR10-2012-0092927 | 2012-08-24 | ||
KR20120092927A KR101480015B1 (ko) | 2012-08-07 | 2012-08-24 | 변속 장치 |
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KR950001632U (ko) * | 1993-06-09 | 1995-01-04 | 나종오 | 무단자동변속장치 |
KR970006994A (ko) * | 1995-07-01 | 1997-02-21 | 김태구 | 무단변속기구 |
US7942777B2 (en) * | 2007-06-01 | 2011-05-17 | Manuel Meitin | Continuously variable automatic transmission for heavy trucks, buses and light automobiles |
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KR940011817A (ko) * | 1992-11-26 | 1994-06-22 | 나종오 | 무단자동변속장치 |
KR950001632U (ko) * | 1993-06-09 | 1995-01-04 | 나종오 | 무단자동변속장치 |
KR970006994A (ko) * | 1995-07-01 | 1997-02-21 | 김태구 | 무단변속기구 |
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