JP2010038184A - Transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To eliminate a bearing and a bush of high capacity by removing the point of force (pin) to which load of a connecting rod is applied in a transmission that converts oscillating motion of the connecting rod connected in an eccentric state to an input shaft into intermittent rotation of an output shaft via a one-way clutch. <P>SOLUTION: When the eccentric amount of an eccentric disk 17 with respect to an axis L1 of the input shaft 11 by a speed change actuator is changed, the oscillation angle of the connecting rod 18 is changed and the angle of reciprocating rotation of a driving member 22 is increased and decreased so that the speed change ratio between the input shaft 11 and the output shaft 12 can be changed. A guide shaft 22b of the driving member 22 is slidably engaged in a guide hole 18c of the connecting rod 18, so that the connecting rod 18 does not need to be connected to the driving member 22 via the pin which is the point of force, and the bearing and the bush of high capacity for supporting the load concentrated on the point of force is not required. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a transmission in which a driving member is reciprocally rotated by a connecting rod that rotates eccentrically by an input shaft, and the reciprocating rotation of the driving member is extracted as an intermittent rotation of an output shaft by a one-way clutch.

Such a transmission is known from Japanese Patent Application Laid-Open No. 2004-228561. The variable transmission eccentricity mechanism includes a pinion holder that forms a ring gear that is eccentric with respect to the axis of the input shaft inside the input shaft that is connected to the engine and rotates, and is rotatably fitted in the ring gear. A circular pinion housing recess is formed on the outer periphery of the ring, and a pinion rotatably supported by the pinion housing recess is engaged with the ring gear. When the pinion is rotated by the electric motor, the pinion that meshes with the ring gear moves along the ring gear together with the pinion holder, and the amount of eccentricity of the pinion axis relative to the axis of the input shaft increases or decreases. Therefore, by connecting the other end of the connecting rod having one end connected to the axis of the pinion to the output shaft via the one-way clutch, the output shaft rotates intermittently as the connecting rod reciprocates.
JP-A-2005-502543

  By the way, in the above conventional one, since the tip of the connecting rod is coupled to the outer race of the one-way clutch through a pin serving as a power point, a large capacity bearing or There was a problem that required a bush.

  In addition, when the above-mentioned conventional one is used as a transmission for an automobile, the connecting rod largely swings inside the casing of the transmission, which causes problems such as heat generation and a decrease in efficiency due to oil agitation. Also, if the position of the output shaft (difference shaft) is increased in order to ensure the minimum ground clearance of the vehicle, the angle of the ball joint of the drive shaft connected to the drive wheel increases, resulting in decreased durability, increased vibration, decreased efficiency, etc. A problem occurs. In order to avoid this, if the one-way clutch of the output shaft is downsized to secure the minimum ground clearance, there is a problem that the durability of the one-way clutch is lowered or the torque capacity is insufficient.

  The present invention has been made in view of the above circumstances, and in a transmission that converts the swinging motion of a connecting rod eccentrically connected to an input shaft into intermittent rotation of an output shaft via a one-way clutch, the load of the connecting rod The purpose is to abolish the force point (pin) applied to eliminate large bearings and bushes.

  To achieve the above object, according to the first aspect of the present invention, an input shaft connected to a drive source and rotating, an eccentric disk rotating eccentrically in conjunction with rotation of the input shaft, and the input A speed change actuator that changes the amount of eccentricity of the eccentric disk with respect to a shaft, a connecting rod that is rotatably fitted to the outer periphery of the eccentric disk, and a drive member that is slidably fitted to the connecting rod and reciprocally rotates. And a transmission comprising an output shaft connected to the drive member via a one-way clutch.

  According to the configuration of the first aspect, when the eccentric disk is eccentrically rotated in conjunction with the rotation of the input shaft connected to the drive source, it is slidable on the connecting rod that is relatively rotatably fitted to the outer periphery of the eccentric disk. When the driving member to be fitted reciprocally rotates, the output shaft connected to the driving member via the one-way clutch rotates intermittently. At this time, if the eccentric amount of the eccentric disk with respect to the input shaft is changed by the speed change actuator, the speed ratio between the input shaft and the output shaft can be changed by increasing or decreasing the reciprocating rotation angle of the drive member. Since it is not necessary to connect the connecting rod to the drive member via a pin serving as a power point, a large-capacity bearing or bush for supporting a load concentrated on the power point is not required.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  1 to 6 show a first embodiment of the present invention. FIG. 1 is an overall side view of the transmission (TOP state), FIG. 2 is an overall side view of the transmission (LO state), and FIG. FIG. 4 is a cross-sectional view taken along the line 3-3 in FIG. 1, FIG. 4 is a diagram for comparing the TOP state and the LO state, FIG. 5 is a diagram for explaining the operation in the TOP state, and FIG.

  As shown in FIGS. 1 and 3, the continuously variable transmission T according to the present embodiment includes an input shaft 11 and an output shaft 12 arranged in parallel, and the rotation of the input shaft 11 is decelerated or increased. And intermittently transmitted to the output shaft 12. An input shaft 11 that rotates by being connected to a drive source 13 such as an engine passes through a hollow rotary shaft 14a of a speed change actuator 14 such as an inner rotor type electric motor, and a pinion 15 is provided at the tip thereof. . The rotor 14b of the speed change actuator 14 is fixed to the rotating shaft 14a, and the stator 14c is fixed to the housing. The rotation shaft 14 a of the speed change actuator 14 can rotate at the same speed as the input shaft 11 of the drive source 13 and can rotate relative to the input shaft 11 at a different speed. A crescent moon-shaped crank member 16 is fixed to the rotating shaft 14 a of the speed change actuator 14.

  The crank member 16 is formed with a circular pinion storage hole 16a into which the pinion 15 is fitted so as to be relatively rotatable. A tooth tip of the pinion 15 is formed at a portion where the pinion storage hole 16a opens on the outer peripheral surface of the crank member 16. Exposed. Therefore, the tooth tip of the pinion 15 is in sliding contact with the inner peripheral surface of the pinion housing hole 16a except for the portion exposed from the opening of the outer peripheral surface of the crank member 16. Further, since the hollow rotation shaft 14a of the speed change actuator 14 which is the rotation center of the crank member 16 is coaxial with the input shaft 11 (that is, the center of the pinion 15), the crank member 16 is centered on the pinion 15 when the speed change actuator 14 is driven. As eccentric rotation.

  In the process in which the crank member 16 rotates eccentrically about the pinion 15, the eccentricity of the eccentric disk 17 with respect to the axis L1 of the input shaft 11 is the maximum state (see FIGS. 1 and 4A). The LO state (see FIGS. 2 and 4B) is when the eccentric amount of the eccentric disk 17 is minimum (in the embodiment, the eccentric amount = 0).

  An eccentric disk 17 in which a ring gear 17 a is formed eccentrically inside a disk-shaped member is provided in a state where the ring gear 17 a is fitted to the outer periphery of the crank member 16 and meshed with the pinion 15. The outer peripheral surface of the crank member 16 is in sliding contact with the tooth tip of the ring gear 17 a of the eccentric disk 17. A ring portion 18 a provided at one end of the connecting rod 18 is fitted to the outer peripheral surface of the eccentric disk 17 via a ball bearing 19 so as to be relatively rotatable.

  A ring-shaped drive member 22 is supported on the outer periphery of the output shaft 12 via a one-way clutch 21, and the diameter from the drive member 22 to a guide hole 18 c as a power point extending radially outward from the ring portion 18 a of the connecting rod 18. A guide shaft 22 b extending outward in the direction is slidably fitted through the bush 26. The bush 26 can be omitted. The one-way clutch 21 includes a boss member 23 fixed to the output shaft 12, and the drive member 22 is fitted on the outer periphery of the boss member 23 so as to be relatively rotatable. A plurality of (for example, four) notches 23 a are formed on the outer periphery of the boss member 23, and a wedge-shaped space formed between the notches 23 a and the inner peripheral surface of the drive member 22 is formed. , Balls 25 urged by springs 24 are arranged.

  Next, the operation of the first embodiment of the present invention having the above configuration will be described.

  When the rotation shaft 14 a of the speed change actuator 14 is rotated relative to the input shaft 11 of the drive source 13, the crank member 16 rotates around the axis L <b> 1 of the input shaft 11. At this time, the pinion housing hole 16a of the crank member 16 slides on the tooth tip of the pinion 15, and accordingly, the eccentric disk 17 slides the tooth tip of the ring gear 17a on the outer peripheral surface of the crank member 16, and the ring gear. The position is changed while maintaining the meshing relationship between 17a and the pinion 15.

  FIG. 4A shows a state where the amount of eccentricity of the eccentric disk 17 with respect to the axis L1 is maximized, and at this time, the ratio of the transmission T is in the TOP state. FIG. 4B shows a state where the amount of eccentricity of the eccentric disk 17 with respect to the axis L1 is minimized, and at this time, the ratio of the transmission T is in the LO state.

  FIG. 5 shows the operation when the transmission T is operated in the TOP state.

  As described above, in the TOP state, the eccentric amount of the eccentric disk 17 with respect to the axis L1 is maximized. When the input shaft 11 is driven by the drive source 13 in this state and the rotation shaft 14a of the speed change actuator 14 is rotated at the same speed as the input shaft 11 of the drive source 13, the input shaft 11, the rotation shaft 14a, the crank member 16 and In the state where the eccentric disk 17 is integrated, it rotates eccentrically about the input shaft 11 in the counterclockwise direction (see arrow A).

  While rotating from FIG. 5A through FIG. 5B to the state of FIG. 5C, the ring portion 18a is supported on the outer periphery of the eccentric disk 17 via the ball bearing 19 so as to be relatively rotatable. The connecting rod 18 rotates the driving member 22 having its guide hole 18c slidably fitted to the guide shaft 22b in the clockwise direction (see arrow C '). 5A and 5C show both ends of the swing of the drive member 22 in the direction of the arrow C ′. At this time, the balls 25 of the one-way clutch 21 are pushed out while compressing the springs 24 from the wedge-shaped notches 23a between the drive member 22 and the boss member 23, so that the drive member 22 is pressed against the boss member 23. Slipping and the output shaft 12 does not rotate.

  When the pinion 15 further rotates, the eccentric disk 17 in which the ring gear 17a is engaged with the pinion 15 is guided by the outer peripheral surface of the crank member 16 and eccentrically rotates counterclockwise (see arrow A). While rotating from the state shown in FIG. 5C to the state shown in FIG. 5A, the ring portion 18a is supported on the outer periphery of the eccentric disk 17 via the ball bearing 19 so as to be relatively rotatable. The connecting rod 18 swings the drive member 22 having the guide hole 18c slidably fitted to the guide shaft 22b in the counterclockwise direction (see arrow C). FIG. 5C and FIG. 5A show both ends of the swing of the drive member 22 in the direction of arrow C. At this time, the balls 25 of the one-way clutch 21 are sandwiched between wedge-shaped notches 23a between the drive member 22 and the boss member 23, and the rotation of the drive member 22 is transmitted to the output shaft 12 via the boss member 23. Therefore, the output shaft 12 rotates counterclockwise (see arrow D).

  As described above, when the drive member 22 reciprocates as the eccentric disk 17 rotates eccentrically, the output shaft 12 rotates counterclockwise only when the rotation direction of the drive member 22 is counterclockwise (see arrow C). The output shaft 12 rotates intermittently (see arrow D).

  FIG. 6 shows the operation when the transmission T is operated in the LO state. At this time, since the axis L1 of the input shaft 11 coincides with the center of the eccentric disc 17, the eccentric amount of the eccentric disc 17 with respect to the input shaft 11 becomes zero. When the input shaft 11 is driven by the drive source 13 in this state and the rotation shaft 14a of the speed change actuator 14 is rotated at the same speed as the input shaft 11 of the drive source 13, the input shaft 11, the rotation shaft 14a, the crank member 16 and In a state where the eccentric disk 17 is integrated, the disk rotates about the input shaft 11 in the counterclockwise direction (see arrow A). However, since the eccentric amount of the eccentric disk 17 is zero, the swing angle of the connecting rod 18 is also zero, and the output shaft 12 does not rotate.

  Therefore, if the speed change actuator 14 is driven and the position of the crank member 16 is set between the TOP state in FIG. 4A and the LO state in FIG. 4B, the zero ratio and an arbitrary ratio between the predetermined ratios are obtained. Can be operated.

  As described above, since the connecting rod 18 is connected to the drive member 22 via the guide hole 18c and the guide shaft 22b, it is not necessary to connect the connecting rod 18 to the drive member 22 via a pin serving as a power point. Large-capacity bearings and bushes are not required to support concentrated loads.

  7 to 12 show a second embodiment of the present invention. FIG. 7 is an overall side view of the transmission (TOP state), FIG. 8 is an overall side view of the transmission (LO state), and FIG. 7 is a cross-sectional view taken along line 9-9 in FIG. 7, FIG. 10 is a diagram for comparing the TOP state and the LO state, FIG. 11 is an operation explanatory diagram in the TOP state, and FIG. 12 is an operation explanatory diagram in the LO state.

  In the first embodiment, the guide hole 18 c of the connecting rod 18 and the guide shaft 22 b of the drive member 22 that are slidably fitted to each other are arranged on the axis line connecting the input shaft 11 and the output shaft 12. However, in the second embodiment, the guide hole 18c of the connecting rod 18 and the guide shaft 22b of the drive member 22 are arranged at positions shifted from the axis. Other configurations of the second embodiment are the same as those of the first embodiment.

  Therefore, in the TOP state shown in FIG. 11, the drive member 22 rotates counterclockwise (see arrow C) during the period of FIGS. 11A to 11C, and the output shaft 12 rotates counterclockwise (arrow D). The drive member 22 rotates clockwise (see arrow C ′) during the period of FIGS. 11C to 11A, and the output shaft 12 stops.

  The operational effects of the second embodiment are basically the same as those of the first embodiment. However, according to the second embodiment, the extension line of the guide shaft 22b of the drive member 22 is an eccentric disk. 17 is directed outward in the radial direction, so that even if the input shaft 11 and the output shaft 12 are brought close to each other, the distal end of the guide shaft 22b of the drive member 22 and the eccentric disk 17 are secured while ensuring the stroke of the connecting rod 18. Interference can be prevented and the transmission T can be reduced in size.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, in the transmission T according to the embodiment, the output shaft 12 rotates intermittently, but the plurality of transmissions T share the input shaft 11 and the output shaft 12, and the phase of the crank member 16 is shifted in the circumferential direction. If juxtaposed in this manner, the pitch of the intermittent rotation of the output shaft 12 can be reduced and the output shaft 12 can be smoothly rotated.

  In the embodiment, the guide hole 18c is provided on the connecting rod 18 side and the guide shaft 22b is provided on the drive member 22 side. However, the relationship between the guide hole and the guide shaft can be reversed.

  In the embodiment, the rotary shaft 14a of the speed change actuator 14 is rotated at the same speed as the input shaft 11 of the drive source 13. However, the rotor 14b of the speed change actuator 14 is mechanically connected to the input shaft 11 of the drive source 13 by a clutch or the like. May be combined.

  In the first embodiment, a bush in which the guide shaft 22b of the drive member 22 is slidably fitted may be provided in the guide hole 18c of the connecting rod 18.

Overall side view of the transmission according to the first embodiment (TOP state) Similarly, overall side view of transmission (LO state) 3-3 sectional view of FIG. Diagram comparing TOP and LO states Action diagram in TOP state Action diagram in LO state Overall side view of transmission according to second embodiment (TOP state) Similarly, overall side view of transmission (LO state) Sectional view taken along line 9-9 in FIG. Diagram comparing TOP and LO states Action diagram in TOP state Action diagram in LO state

Explanation of symbols

11 Input shaft 12 Output shaft 13 Drive source 14 Shift actuator 17 Eccentric disk 18 Connecting rod 21 One-way clutch 22 Drive member

Claims (1)

An input shaft (11) connected to the drive source (13) and rotating;
An eccentric disk (17) that rotates eccentrically in conjunction with the rotation of the input shaft (11);
A speed change actuator (14) for changing the amount of eccentricity of the eccentric disk (17) relative to the input shaft (11);
A connecting rod (18) which is fitted to the outer periphery of the eccentric disk (17) in a relatively rotatable manner;
A drive member (22) slidably fitted to the connecting rod (18) and reciprocally rotated;
An output shaft (12) connected to the drive member (22) via a one-way clutch (21);
A transmission comprising:

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