KR0122117B1 - Stepless transmission - Google Patents

Abstract

Transmission for indefinitely variable speed changing according to the present invention includes a transmission gear box(2) secured on the input shaft(1) which is delivered power from the engine(E). A speed-changing control unit(4) is delivered the changed revolution torque from the transmission gear box(2) and the unchanged revolution torque from the engine(E). And then the change of speed corresponding the difference between the changed torque and the unchanged torque is achieved by means of the control unit(4). The changed revolution torque is delivered from the control unit(4) to the output shaft(3). The transmission gear box(2) consists of the sun gear(5) formed on the input shaft(1), the plurality of conical planetary gears(6) engaged with the sun gear(5), ring gear(7) moving to the longitude direction of the planetary gears(6) to change the diameter of the planetary gears(6), support carrier(8), and output carrier(9).

Description

Continuously variable transmission

1 is a schematic diagram showing the structure of a continuously variable transmission according to a first embodiment of the present invention.

2 is a schematic diagram showing the structure of a continuously variable transmission according to the first embodiment of the present invention.

3 is a graph showing a speed relation equation output from the planetary gear unit according to the configuration of the present invention.

4 is a table showing the operating elements operated at each level when the continuously variable transmission of the present invention is switched to the neutral, low speed and high speed levels.

* Explanation of symbols for main parts of the drawings

1: input shaft 2: transmission mechanism

3: drive shaft 4: shift control mechanism

5: Sun gear 6: Planetary roller

7: Moving ring 8: support carrier

9: output carrier 10: bevel gear

11: axis of rotation 12: transfer drive gear

13: Moving mechanism 14: Transfer driven gear

15: Planetary gear unit 16: Sun gear

17: Pinion gear 18: Friction plate

The present invention relates to a transmission for shifting power transmitted from a power generating device to a driving means. Particularly, the present invention relates to a continuously variable transmission of a friction vehicle type, which has a compact size, excellent power transmission efficiency, and a wide range of transmission. It is about.

In general, a driving means such as a vehicle uses a transmission to adjust the output of the power and the rotational speed of the power generating means for generating power to match the load and the operating state of the driving means.

Transmissions used for this purpose generally include a manual transmission adapted to manually adjust the shift stage appropriately according to the driving state of the drive means, and an automatic transmission in which the shift stage is automatically adjusted according to the driving state of the driving device. Since transmissions have their own advantages, they are appropriately selected and used according to necessity. In particular, automatic transmissions are gradually used for the reasons of convenience in using these transmissions in vehicles.

However, the automatic transmission also sets a predetermined shift section in accordance with the driving state of the driving device, that is, the driving state of the vehicle, and allows the shift to be automatically performed while various operating elements are selectively operated. Therefore, since most automatic transmissions must be equipped with a plurality of planetary gear units, a plurality of operating elements for controlling the operation of each component of the planetary gear units, and a complicated control device for controlling these operating elements, the configuration is complicated. In addition, it is inconvenient that it is difficult to universally install the automatic transmission composed of one model to all the driving means due to its large volume, and also is installed on the driving means such as a vehicle because of the large volume of the automatic transmission. If the installation takes up a lot of space, there was a difficulty in installing such an automatic transmission in the manufacturing process of the vehicle.

In addition, since the shifting process is not performed linearly in the existing automatic transmission, switching from one shifting stage to another shifting stage cannot be performed continuously, which causes excessive force on the engine, which is a power generator, and the shifting. There was a problem in that the riding comfort due to shock and vibration generated at the time is not good.

In order to solve the problems of the automatic transmission, the shifting is made continuously according to the driving condition of the vehicle, so that the riding comfort due to the shock and vibration generated during the shifting can be prevented and the engine is unduly operated. One continuously variable transmission has been proposed as an invention such as US Pat. No. 4,641,548.

However, since the continuously variable transmission uses a plurality of discs and pistons, it is bulky and has a structure in which a plurality of continuously variable transmissions are arranged on the same axis to increase power transmission efficiency. There is a problem that it is not easy to apply to a passenger car that is restricted by a lot of installation space due to a long time, and also because the cost is expensive, there was an undesirable problem in terms of economy.

Therefore, the present invention solves the problems described above, the volume is small and its operation element is small, the configuration is simple, the power transmission efficiency is excellent, the control is simple, and the transmission range that the transmission range is widened to provide an object. have.

The continuously variable transmission of the present invention for achieving the above object comprises a sun gear provided on an input shaft for transmitting power generated from an engine, and a cone having a predetermined distance along the circumferential direction around the sun gear. A plurality of planetary rollers, which are arranged to contact the conical surfaces of the planetary rollers, are moved along the longitudinal direction of the planetary rollers by a moving means, and the operating diameter of the planetary rollers is moved by the longitudinal movement of the planetary rollers. The carrier which transmits the rotational force which is shifted in the planetary roller while being connected to each other by supporting the moving ring and the planetary gears arranged around the sun gear by varying the revolving speed of the planetary roller so that the output speed is variable. The primary shift is made by a shift mechanism consisting of: The primary shift made by one shift mechanism is output to the shift control mechanism through the carrier so that the primary shift as desired is finally achieved by the mutual combination of the shift mechanism and the shift control mechanism.

The conical planetary rollers constituting the transmission mechanism are arranged such that their circumscribed circle is in equilibrium with the input shaft, so that the distance between the circumscribed circles which are in contact with the plurality of planetary rollers simultaneously from the input shaft is the same over the entire length of the planetary roller. The fixed diameter of the moving ring can move along the longitudinal direction of the planetary roller in a state in which the outer ring of the planetary roller is in contact with the same pressure. In this way, the moving ring is moved along the longitudinal direction of the planetary roller, the diameter of the planetary roller inscribed in the moving ring is linearly variable along the conical surface of the planetary roller, the support diameter of the planetary roller is variable The idle speed is also linearly varied and outputted accordingly.

On the other hand, the shift control mechanism is a low speed control mechanism comprising a planetary gear unit connected to the output shaft and a first clutch for controlling the operation of the planetary gear unit, and a high speed control means comprising a second clutch provided on the output shaft. While each of the planetary gear units constituting the low speed control means and the second clutch constituting the high speed control means are directly connected in parallel with the output carrier of the transmission mechanism, the planetary gear unit has a first clutch. It is also directly connected to the input shaft receives power from the engine through the planetary gear unit has a structure having two input stages by the rotational force controlled by the transmission mechanism and the rotational force of the engine at the same time.

According to the selective operation of the high speed control mechanism and the low speed control mechanism of the shift control mechanism, the rotation speed primarily shifted through the shift mechanism is operated when the first clutch is operated in the shift control mechanism and the second clutch is operated. Depending on the operation, the final shift is made and output.

That is, when the first clutch for low speed is operated by the lock, the rotational force shifted from the transmission mechanism and the rotational force of the engine are input together to the planetary gear unit. In this planetary gear unit, the rotational speed and engine input from the transmission mechanism are input. According to the size of the rotation speed transmitted from the outputted combined speed at the appropriate combination ratio. Therefore, when the moving ring moves along the surface of the planetary roller and the diameter of the planetary roller in contact with the moving ring is changed in the transmission mechanism operating by receiving the rotational speed of the same engine, the output rotation speed of the transmission mechanism is changed accordingly. The rotation speed thus shifted is transmitted to the planetary gear unit of the shift control mechanism so that the shift state is changed accordingly.

That is, in the planetary gear unit, since the primary shift force and the rotational force of the engine are combined and shifted to the output shaft, the rotation speed input from the shift mechanism to the planetary gear unit is changed. According to the output speed of the planetary gear unit is to be variable. The planetary gear unit is operated by the first clutch being locked so that the rotational force shifted from the transmission mechanism and the rotational force of the engine are simultaneously transmitted to the planetary gear unit.

On the other hand, when the lock of the first clutch is released and the second clutch is operated instead, the rotational force of the engine is not transmitted to the planetary gear unit of the low speed control mechanism, and the planetary gear unit is in an idling state. The rotational force output from the transmission mechanism is transmitted directly to the output shaft through the second clutch. Therefore, in this state, the output shifted from the transmission mechanism is transmitted to the output shaft as it is, without being shifted again in the middle, so that the rotational force of a faster speed is output than when the first clutch is locked. .

Therefore, when the second clutch is locked, the final output is operated at a higher speed than when the first clutch is locked, and gradually becomes a high speed as the output rotation speed of the transmission mechanism is increased. will be.

Hereinafter, with reference to the accompanying drawings, the present invention will be described in detail.

FIG. 1 schematically shows a first embodiment according to the present invention, and FIG. 2 schematically shows a second embodiment of the present invention, and as shown in these figures, power from the engine E is shown. It consists of a transmission mechanism (2) installed on the input shaft (1) to be transmitted, and a transmission control mechanism (4) installed on the output shaft (3) which is connected to the transmission mechanism (2) by gear engagement and outputs a left torque when the transmission is completed. have.

Here, the transmission mechanism 2 includes a sun gear 5 directly installed on the input shaft 1 and a plurality of conical planetary rollers which are arranged at predetermined intervals along the circumferential direction while being engaged with the sun gear 5. 6) a movement disposed on the outer side of the planetary rollers 6 so as to be in frictional contact with the surface of each planetary roller 6 at a predetermined pressure, the movable rollers being movable along the longitudinal direction of the planetary rollers 6; A ring 7 and a plurality of planetary rollers 6 are connected to each other to support each other, and are composed of a support carrier 8 and an output carrier 9 for outputting the rotational force shifted in these planetary rollers 6.

In addition, the planetary roller 6 and the sun gear 5 have a gear 10 provided in the planetary roller 6 so that teeth thereof mesh with the sun gear 5 so as to receive a rotational force from the sun gear 5. The support carrier 8 and the output carrier 9 support the front and rear sides of the planetary roller 6 so as to rotate, and the output carrier 9 is powered by the output shaft 3. It is composed of a structure provided with a transfer drive gear (12) for transmitting a.

On the other hand, the movable ring 7 is fixed so as not to rotate itself, while the planetary roller 6 is received from the sun gear 5 while frictionally contacting the planetary roller 6 at a predetermined pressure inside the movable ring 7. In addition to the rolling movement by the driving force, it is provided so as to reciprocate in a linear direction by a moving means 13 such as a hydraulic cylinder, a solenoid or a worm gear. Therefore, the movable ring 7 does not rotate while receiving power while performing the same function as the ring gear in the general planetary gear unit, and only supports the planetary roller 6 which is engaged with the sun gear 5 and receives the rotational force, thereby providing frictional force. By adding the planetary roller 6 is to rotate while rotating.

Then, as described above, the movable ring 7 fixed to have a constant diameter has a diameter of the plurality of planetary rollers 6 having a different diameter along the longitudinal direction, that is, conical, by the moving means 13. In order to be able to move while contacting the outer surface at a uniform pressure, as shown in FIGS. 1 and 2, the outer surface S of each of the planetary rollers 6 should be disposed in equilibrium with the input shaft 1.

On the other hand, the planetary roller (6) does not only play the role of the planetary gear in the general planetary gear unit, the diameter of the point of contact with the movable ring (7) while rotating by receiving power from the sun gear (5) As the variable speed changes, the revolution speed rotating along the inside of the movable ring 7 is varied, and serves to vary the rotation speed discharged through the output carrier 9 which interconnects the planetary rollers 6. Perform.

Accordingly, the moving ring 7 connected to the moving means 13 moves along the surface along the longitudinal direction of the planetary roller 6 having a conical shape by the expansion and contraction of the moving means 13. 7) and the support of the planetary roller 6 is in contact with each other, and as the support points of the movable ring 7 and the planetary roller 6 are variable as described above, the planetary roller 6 is moved by the movable ring 7 The rotational diameter of the rotor is linearly variable, and the circumferential speed of the planetary roller 6 rotating along the inner surface of the movable ring 7 is also linearly changed due to the linear change in diameter. It will be done.

That is, when the planetary roller 6 rotates by the rotational force transmitted from the sun gear 5 through the gear 10, the moving ring 7 supported from the outside of the planetary roller 6 is a planetary roller. The planetary roller 6 is rolled along the inner surface of the movable ring 7 due to the force transmitted from the sun gear 5 because it can move along the longitudinal direction of (6) but cannot rotate. While rotating, the rotating speed of the planetary roller 6 is determined by the rotational speed transmitted from the sun gear 5, but the rotating speed of the planetary roller 6 moves under the same rotational speed. As the diameter of the planetary roller 6 inscribed in the ring 7 is varied, it will vary. Therefore, as described above, as the diameter of the planetary roller 6 changes linearly, the revolving speed of the planetary roller 6 rotating along the inner surface of the moving ring 7 also varies linearly.

Therefore, assuming that the load applied to the output shaft 3 is the same in the state in which the engine is operated under the same condition at any particular point of time, the gear 10 of the planetary roller 6 engaged with the sun gear 5 is The input rotational speed becomes constant, and the rotation speed of the planetary roller 6 integrated with the gear 10 is also the same, but the inner ring is inscribed to the moving ring 7 with the moving ring 7 as a supporting point. Since the diameter of the rotating planetary roller 6 varies with the movement of the moving ring 7, the planetary roller 6 is supported by the moving ring 7 and rotates according to the position of the moving ring 7. The moving distance is changed, and the moving distance of the planetary roller 6 is transmitted to the output carrier 9 connecting the plurality of planetary rollers 7 through the rotary shaft 11, as a result Transfer driver gear provided in the output carrier (9) The circumferential speed of 12) is changed.

Therefore, the rotation speed output from the planetary roller 6 is changed according to the contact diameter of the moving ring 7 and the planetary roller 7 so that the rotational speed output from the transmission mechanism 2 is variable.

To supplement the function of the planetary rollers 6 described above, the plurality of planetary rollers 6 are supported by the movable ring 7 while being engaged with the sun gear 5 and these planetary rollers 6 are supported. Since the planets are connected to each other by the carriers 8 and 9, the planetary rollers 6 engaged with the sun gears 5 are rotated by the rotational force transmitted from the sun gears 5. Since the roller 6 is held in close contact with the non-rotating moving ring 7 and is connected to each other by the carriers 8 and 9, the planetary rollers 6 are eventually removed from the sun gear 5. The rotating force is to rotate while riding on the inner surface of the mobile ring (7). At this time, the rotation speed input from the sun gear 5 to the gear 10 of the planetary roller 6 is constant, but as the support point of the movable ring 7 supporting the planetary roller 6 is variable, the movable ring Since the rotation diameter of the planetary roller 6 with respect to (7) is different, the revolution speed of the planetary roller 6 which revolves with the output carrier 9 on the inner surface of the movable ring 7 is variable. Will be.

The shifted speed by the planetary roller 6 is represented by an enlarged circumferential speed in the transfer drive gear 12 which is provided in the output carrier 9 and has a diameter much larger than that of the planetary roller 6. The final shift result is transmitted to the shift control mechanism 4 through the transfer drive gear 12.

Therefore, the state in which the output speed of the transmission mechanism 2 varies linearly is connected to the plurality of planetary rollers 6 when the movable ring 7 is in contact with the larger diameter of the planetary rollers 6. The revolving speed of the output carrier 9 is increased, and when the diameter of the movable ring 7 is in contact with the smaller diameter of the rollers 6, the output carriers 9 interconnecting the planetary rollers 6 with each other. The idle speed becomes smaller. Therefore, as the moving ring 7 moves from the larger diameter to the smaller diameter of the rollers 6, the rotational speed of the output carrier 9 and the transfer drive gear 12 connected to the output carrier 9 is increased. Will be reduced.

As such, the movable ring 7 moves along the surface of the planetary roller 6 by the operation of the conveying mechanism 13 in the longitudinal direction, whereby the support point of the planetary roller 6 with respect to the movable ring 7 is supported. Even if the same rotational speed is inputted to the gear 10 of the planetary roller 6 to be variable, a difference occurs in the amount of movement of the planetary roller 6 moving on the inside of the moving ring 7. The difference of the movement amount with respect to the moving ring 7 of (6) is soon expressed as a shift.

On the other hand, the shift control mechanism 4 is a low-speed control means consisting of a transfer driven gear (14) provided on the output shaft (3), a planetary gear device (15) and a first clutch (C1), and The transfer driven gear 14 is engaged with the transfer drive gear 12 of the output carrier 9 and shifted in the transmission mechanism 2 while being composed of high speed control means composed of two clutches C2. The speed is transmitted to the shift control mechanism 4.

The transfer driven gear 14 has a structure in which the planetary gear unit 15 constituting the low speed control means and the second clutch C2 constituting the high speed control means are connected in parallel to each other. 15, the sun gear 16 is directly connected to the transfer driven gear 14, the pinion gear 17 is connected to one friction plate 18 of the first clutch (C1), the first clutch The other friction plate 19 of (C1) is directly connected to the high speed gear 22 installed on the input shaft 1 through the carrier 20 and the direct gear 21, while the ring of the planetary gear unit 15 is connected. The gear 23 has a structure connected to the output shaft 3.

Therefore, the planetary gear unit 15 is composed of two elements of the sun gear 16 and the pinion gear 17, the input end of the driving force is transmitted, the output end is a ring gear 23 connected to the output shaft (3) will be.

Therefore, the primary gear shifted from the transmission mechanism 2 and input to the sun gear 16 of the planetary gear unit 15 and the high speed gear 22 and the direct gear 21 and the first gear 21 from the input shaft 1. The rotational speed inputted to the pinion gear 17 of the planetary gear unit 15 through the clutch C1 is combined shifted in the planetary gear unit 15, and finally the rotational speed that is changed to the ring gear 23 is changed. It will be transmitted to the output shaft (3) through.

In the continuously variable transmission of the present invention having such a structure, it is possible to vary the installation state of the planetary roller 6 and the central shaft 11 according to each embodiment, that is, of the present invention as shown in FIG. In the first embodiment, the planetary roller 6 and the central shaft 11 are separated from each other, and a bearing 24 for assisting smooth rotation between the planetary roller 6 and the central shaft 11 is provided. In the second embodiment of the present invention shown in FIG. 2, the planetary roller 6 and the central shaft 11 are integrated with each other, and both ends of the central shaft 11 are integrated. Bearings 25 and 26 are provided in the shaft to assist smooth rotation of the central shaft 11.

As in the second embodiment, the central shaft 11 and the planetary rollers 6 are integrally formed so that the planetary shafts 11 and the planetary rollers 6 are separated from each other. Since the length of the roller 6 can be lengthened, when the length of the planetary roller 6 becomes longer, the speed change section becomes longer, so that a speed ratio larger than that of the first embodiment can be obtained.

There is no other structural difference between the first embodiment and the second embodiment except for the structure of the planetary roller 6 and the central axis 11.

Each step of the stepless transmission process of the transmission of the present invention having the structure as described above is as follows. Here, the operating relationship of each operating element that operates to achieve each shift stage is shown in the table shown in FIG.

Before explaining in detail the process of allowing the transmission of the present invention to continuously variable transmission, to explain the operational features according to the structural conditions in order to help the understanding of the shifting process made in the continuously variable transmission of the present invention, The continuously variable transmission of the invention allows the driving force of the engine (E) to be primarily shifted in the transmission mechanism (2), and the result of the primary shift is transmitted to the shift control mechanism (4). The final shift of the bar is to be obtained. In this shifting process, the process from neutral to low speed to medium speed is performed by locking the first clutch C1, and the process from medium speed to high speed is performed by the first clutch. (C1) is made to be released and instead to lock the second clutch (C2).

In addition, in the operational feature of the planetary gear unit 15 which is operated when the first clutch C1 is locked, the input end to which the driving force is transmitted as described above is the sun gear 16 and the pinion gear 17. Since the two speeds of the two elements are established, a specific speed relation equation is established. That is, as described above, the driving force is simultaneously input to the sun gear 16 and the pinion gear 17, and the The speed relation obtained from the planetary gear unit 15 to which the shifted output is transmitted is

(1 + λ) ω _c = λω _s + ω _{R ..................... ..........................(One)}

Where λ = tooth of sun gear / tooth of ring gear

ω _c = rotational speed of the carrier connecting the pinion gear

ω _s = Rotational speed of sun gear

ω _R = Rotational speed of ring gear

It is expressed as

If we rearrange the speed relation of planetary gear,

...................(2)

do.

Figure 4 shows a graphical representation of the relationship. As can be seen from this graph, the planetary gear unit 15 having the input and output ends of the driving force as described above is connected to the pinion gear 17. because the velocity (ω _c) of the carrier constant, wherein ω _c that is, if the speed of the sun gear 16 increases ω _R that is, the speed of the ring gear 23 being reduced, dwindles the other hand, the speed of the sun gear 16, ring The rotational speed of the gear 23 is to be increased.

And the rotational speed ratio of the sun gear 16 to the pinion, that is, end If more than The value is negative. This is because ω _c, that is, the rotational speed value of the carrier connected to the pinion gear 17 is a common denominator, so that when the value of the speed ω _s of the sun gear 16 increases above a predetermined value, ω _R becomes negative. The negative value of ω _R means that the rotation of the ring gear 23 is reversed. This functional feature can be easily recognized from the graph of FIG.

The planetary gear unit 15 used in the present invention has the above operational characteristics, and in the following description, the operation process according to each shift state is specifically provided on the premise of using the planetary gear unit 15. Explain.

Neutral state (initial state)

Neutral state of the continuously variable transmission according to the present invention can be made of two processes, the first operation process is the first clutch (C1) and second installed on the output shaft (3) as shown in the table of FIG. When the clutch C2 is released without locking, the transmission drive 2 is transferred from the transmission mechanism 2 to the transfer driven gear 14 via the transfer drive gear 12 provided in the output carrier 9 of the transmission mechanism 2. Even when the power is transmitted, since the first clutch C1 and the second clutch C2 are released so as not to transmit power, the transfer driven gear 14 is idling and the power is output to the output shaft 3. It will not be delivered.

Therefore, as described above, when the first clutch C1 and the second clutch C2 are unlocked, power is not transmitted to the output shaft 3, and thus the neutral state does not rotate.

On the other hand, in the second operation process of forming a neutral state, the diameter of the planetary roller 6 is larger in the state in which the second clutch C2 is unlocked and only the first clutch C1 for low speed is locked. When the moving ring 7 is positioned on the neutral line C formed near the tip, the rotational force primarily shifted by the transmission mechanism 2 is transferred to the transfer drive gear 12 and the transfer driven gear 14. The rotational force of the input shaft 1 is directly connected to the high speed gear 22 through the first clutch C1 which is input to the sun gear 16 of the planetary gear unit 15 through the lock operation. Since 21 and the first clutch C1 are input to the pinion gear 17 of the planetary gear unit 15, the drive speed of the sun gear 16 and the drive speed of the pinion gear 17 are balanced. The sun gear 16 and the pinion gear 17 rotate together, and the outer ring machine 23, it is not transmitting the driving force.

Therefore, since the ring gear 23 does not transmit power to the output shaft 3, the ring gear 23 is in a neutral state in which the output shaft 23 is not driven.

That is, when the first clutch C1 is locked and the movable ring 7 is positioned at the neutral line C, the rotational force of the engine primarily shifted by the transmission mechanism 2 is output by the output carrier ( 9) through the transfer drive gear 12 and the transfer driven gear 14 to the sun gear 16 of the planetary gear unit 15, as well as the high-speed gear 22 and the direct gear (22) provided in the input shaft (1) 21) and the rotational force of the engine is input to the pinion gear 17 of the planetary gear unit 15 without being shifted through the first clutch C1, and thus the primary shift is made in the transmission mechanism 2. In the planetary gear unit 17 which receives the rotational force and the rotational force of the engine at the same time, the ratio of the rotational speed of the sun gear 16 and the rotational speed of the pinion gear 17 rotating around the sun gear 16 is the pinion gear 17. Does not transmit rotational force to the ring gear 23 surrounding Instead, the sun gear 16 and the pinion gear 17 are rotated together. Therefore, since the ring gear 23 does not drive the output shaft 3, it is in a neutral state.

As described above, when the moving ring 7 moves from the neutral line C to the smaller diameter of the planetary roller 6 while the first clutch C1 is locked, shifting is performed in the forward direction. When the diameter of the planetary roller 6 moves toward the larger side of the neutral line C, the shift is made in the reverse direction, and the forward and reverse direction switching process will be described later in detail.

Low to medium speed (forward rotation)

When the first clutch C1 is locked in the neutral state as described above, and the moving ring 7 moves from the neutral line C of the planetary roller 6 to a smaller diameter, the moving ring 7 The operating diameter of the planetary roller 6 which is in contact with and is gradually reduced, and when the operating diameter of the planetary roller 6 is reduced in this way, the planetary roller 6 with respect to the moving ring 7 as described above sufficiently. Since the revolving speed of C) decreases as the diameter of the supporting point decreases, the circumferential speed of the output carrier 9 connecting the plurality of planetary rollers 6 to each other decreases, and the output carrier 9 and the transfer are reduced. The rotation speed of the sun gear 16 of the planetary gear unit 15 connected through the drive gear 12 and the transfer driven gear 14 is also gradually reduced.

On the other hand, the rotational speed ratio transmitted from the input shaft 1 to the pinion gear 17 through the high speed gear 22, the direct gear 21 and the first clutch C1 is not equal to the high speed gear 22 and the direct gear ( Since the pinion gear 17 is not changed at all, the pinion gear 17 rotates about the sun gear 16 at a relatively high speed.

Therefore, as shown in the graphs of Equation (2) and FIG. 4, the rotational speed ω _s of the sun gear 16 gradually decreases, in combination with the rotational speed ratio of the pinion gear 17, and thus the ring gear. The rotational speed output through 23 is gradually increased, and as a result, the rotational speed of the output shaft 3 connected to the ring gear 23 is increased.

Therefore, as described above, as the moving ring 7 moves toward the smaller diameter of the planetary roller 6, the rotation speed transmitted to the output shaft 3 through the ring gear 23 gradually increases. .

This state is a process in which the continuously variable transmission according to the present invention is shifted from low speed to medium speed. As described above, since the diameter of the planetary roller 6 to which the movable ring 7 contacts is linearly varied, The rotational speed discharged through the planetary gear unit 15 connected to the planetary roller 6 is also gradually increased. Therefore, the shift from the low speed state to the medium speed is performed without permission.

Medium speed to high speed (forward rotation)

When the medium speed is reached through the above-described process, the movable ring 7 is positioned at the tip portion of the planetary roller 6 having the smallest diameter. In this state, when the lock operation of the first clutch C1 is released and the lock operation of the second clutch C2 is performed, since the first clutch C1 is released, the planetary body is released from the input shaft 1. The rotational force is not transmitted to the pinion gear 17 of the gear unit 15, but the sun gear 16 of the planetary gear unit 15, which is always engaged with the transfer driven gear 14, continues to rotate, Since the pinion gear 17 does not rotate, the planetary gear unit 15 is in an idling state as a whole so that driving force is not transmitted to the ring gear 23.

In this state, when the second clutch C2 for high speed is engaged, the rotational force of the transmission mechanism 2 is transmitted to the output shaft 3 through the transfer driven gear 14. In this process, the transmission mechanism Since the shift force made in (2) is transmitted to the output shaft 3 through the second clutch C2 without being re-decelerated again, the second clutch is increased when the rotation speed output from the transmission mechanism 2 increases. The rotation speed of the output shaft 3 receiving the rotational force through C2 is increased at the same rate.

Therefore, as already described above, as the movable ring 7 moves from the tip of the smaller diameter of the planetary roller 6 to the larger diameter, the output carriers connecting the plurality of planetary rollers 6 to each other. Since the circumferential speed of (9) is increased, this increased rotational speed is transmitted directly to the output shaft 3 through the second clutch C2 to increase its rotational speed.

In this shifting process from the medium speed to the high speed, since the rotational force output from the transmission mechanism 2 is immediately transmitted to the output shaft 3, an intermediate shift means such as a separate planetary gear unit 15 as in the low speed state. It does not go through the complicated shifting process caused by. Therefore, in the case of shifting from the medium speed to the high speed, only the process in which the rotational speed output from the transmission mechanism 2 is transmitted through the second clutch C2 of the shift control mechanism 4 is made.

In addition, since the diameter of the planetary roller 6 is linearly increased even in this high speed shifting process, the speed of the output shaft 3 which is rotated by receiving the output of the planetary roller 6 gradually increases. In this high speed section, the continuously variable shift is made.

Reverse rotation state

In the continuously variable transmission according to the present invention described above in detail while explaining the operation process according to its structural features and as shown in the table in Figure 4, to reverse the output shaft (3) of the continuously variable transmission according to the present invention In this case, when the first clutch C1 is locked in a state in which the second clutch C2 is released, the gear shifted in the transmission mechanism 2 is performed in the same manner as in the shifting process up to medium speed as described above. The rotational force is input to the sun gear 16 of the planetary gear unit 15, and the rotational force of the input shaft 1 is transmitted to the planetary gear unit through the high speed gear 22, the direct gear 21, and the first clutch C1. 15 is input to the pinion gear 17.

Thus, since the equation (2), oil velocity ω _s of the pinion gear 17 of the gear unit 15, as in the same conditions, to which the sun gear 16, the speed ω _s increases above a predetermined value, Has a value of If greater The value of becomes negative.

In this state, since the rotational speed ω _c input to the pinion gear 17 is the same condition, it is determined according to the speed of the sun gear 16, and the critical line of the forward and reverse rotation of the sun gear 16 is That is, the neutral line (C) indicated on the planetary roller (6). Therefore, when the movable ring 7 moves beyond the neutral line C toward the larger diameter, the transfer drive provided in the output carrier 9 supporting the planetary roller 6 according to the principle described above. Since the circumferential speed of the gear 12 is increased, the rotational speed of the sun gear 16 of the planetary gear unit 15 connected to the transfer drive gear 12 is increased above the threshold value and the planetary gear as described above. The rotational direction output through the ring gear 23 of the unit 15 is reversed.

On the other hand, even in the case of high speed forward rotation, the moving ring 7 moves beyond the neutral line C, but in the case of such high speed forward rotation, the point at which the diameter of the moving ring 7 exceeds the neutral line C is the maximum. If it moves to the highest speed, the gear is shifted to the highest speed and the output shaft 3 does not reverse as in the case of reverse rotation. In the case of the above-mentioned high speed forward rotation, the second clutch C2 is locked and the first clutch ( While C1) is released, the first clutch C1 is locked and the second clutch C2 is released during reverse rotation, so that the same state is not achieved during forward and reverse rotation. Will be.

That is, even when the movable ring 7 moves toward the maximum diameter of the planetary roller 6, if the first clutch C1 is not locked and the second clutch C2 is locked, the planetary gear unit 15 Since the above equations (1) and (2) are not applied because they do not operate, the shift state made in the transmission mechanism 2 is transmitted to the output shaft 3 through the second clutch C2 as it is. In the forward high speed, as the moving ring 7 moves toward the larger diameter of the planetary roller 7, the output speed is transmitted to the output shaft 3 as it is, thereby increasing the speed at high speed. There is.

Therefore, the continuously variable transmission according to the present invention does not use a separate direction switching means for switching the forward and reverse rotation, and thus switching the forward and reverse rotation by controlling only the rotation speed output from the transmission mechanism 2, Switching of the rotation is simple and smooth, and the structure of the transmission is simplified and compact as a whole.

As described above, the rotational force generated by the shift is transmitted to the differential gear 28 of the driving means to be driven through the output gear 27 provided at the tip of the output shaft 3, such as a vehicle. It is driven at an appropriate speed according to the state of the load added to the drive means.

As described above, the continuously variable transmission according to the present invention includes a transmission mechanism (2) using a planetary roller (6), and a first clutch (C1), a planetary gear unit (15), and a first gear (C1). The shift control mechanism 4 made of two clutches C2 is connected to each other, and the moving ring 7 of the shift mechanism 2 is simply moved along the surface of the planetary roller 6. Accordingly, the output speed is shifted steplessly, and the forward rotation and the reverse rotation are not additionally provided with any other mechanism, and the position of the above-mentioned moving ring 7 is changed to a large diameter of the planetary roller 6. By simply moving to the side, since the output rotation direction is switched between forward rotation and reverse rotation, the structure becomes extremely simple as a whole. Therefore, even when installed in a drive means that the installation space is not enough, such as a vehicle is less restricted by the volume.

In addition, since only the movement ring 7 needs to be moved as described above, shift control is easy, and the shift range corresponding to the length of the planetary roller 6 is obtained, thereby increasing the shift range.

Claims (2)

A plurality of conical planetary rollers which are frictionally contacted at a predetermined pressure by the reciprocating movable ring 7 which is engaged with the sun gear 5 installed on the input shaft 1 receiving power from the engine E. In the continuously variable transmission having a 6), the moving ring (7) is made while the reciprocating movement of the surface of the planetary roller (6) in the longitudinal direction, the transmission force is transmitted to the output shaft (3), The output carrier 9 for transmitting the rotational force shifted by the planetary roller 6 is provided with a transfer drive gear 12 for transmitting power to the output shaft 3, and the input shaft 1 has the engine ( A high speed gear 22 for directly transmitting the rotational force of E) to the output shaft 3 is directly installed, and a transfer driven gear meshed with the transfer drive gear 12 and the high speed gear 22 on the output shaft 3, respectively. Direct connection with 14 Gear 21 is installed, the transfer driven gear 14 is connected to the second clutch (C2) directly installed on the output shaft (3), the direct gear 21 to interrupt the power transmission of the engine. It is connected to the first clutch (C1), the planetary gear unit 15 is connected between the transfer driven gear 14 and the first clutch (C1), respectively. The planetary gear unit 15 makes a shift corresponding to a difference between the shift rotation speed transmitted through the transfer drive gear 12 and the rotation speed of the engine E, and outputs the shifted rotation force to the output shaft ( 3) continuously variable transmission, characterized in that configured to transmit. According to claim 1, wherein the sun gear 16 of the planetary gear unit 15 is connected to the transfer driven gear 14, the pinion gear 17 of the planetary gear unit 15 is the first clutch (C1) Is connected to one friction plate 18 of the second clutch C2, and the other friction plate 19 of the second clutch C2 is connected to the high speed gear 22 installed on the input shaft 1 via the carrier 20 and the direct gear 21. While connected, the ring gear 22 of the planetary gear unit 15 is a continuously variable transmission, characterized in that made of a structure connected to the output shaft (3).