JP6011972B2 - Power transmission device for vehicle - Google Patents

Description

  According to the present invention, a plurality of power transmission units that shift the rotation of an input shaft connected to a drive source and transmit it to the output shaft are juxtaposed in the axial direction, and each of the power transmission units is separated from the axis of the input shaft. An input side fulcrum that is variable in eccentricity and rotates together with the input shaft, a one-way clutch connected to the output shaft, an output-side fulcrum provided on an outer member of the one-way clutch, the input-side fulcrum and the output The present invention relates to a vehicle power transmission device including a connecting rod that connects side fulcrums.

  Multiple crank type power transmission units that convert the rotation of the input shaft connected to the engine into the reciprocating motion of the connecting rod and convert the reciprocating motion of the connecting rod into the rotational motion of the output shaft by a one-way clutch are juxtaposed in the axial direction. A vehicular power transmission device is known from Japanese Patent Application Laid-Open No. 2004-228561.

JP 2012-251611 A

  By the way, the conventional one-way clutch of the power transmission device for a vehicle supports the outer member coaxially with respect to the inner member by disposing ball bearings on both axial sides of the plurality of rollers. Thus, when each one-way clutch is provided with two ball bearings, not only the number of necessary ball bearings is increased, but two ball bearings are installed at the opposing portions of two adjacent one-way clutches. In order to secure the installation space, there is a problem that the distance between adjacent one-way clutches is widened and the axial dimension of the vehicle power transmission device is increased.

  The present invention has been made in view of the above circumstances, and in a vehicle power transmission device in which crank-type power transmission units are juxtaposed in the axial direction, the interval between two adjacent one-way clutches is narrowed to reduce the axial dimension. The purpose is to do.

  To achieve the above object, according to the first aspect of the present invention, a plurality of power transmission units for shifting the rotation of the input shaft connected to the drive source and transmitting it to the output shaft are juxtaposed in the axial direction. Each of the power transmission units includes an input-side fulcrum that is variable in eccentricity from the axis of the input shaft and rotates together with the input shaft, a one-way clutch connected to the output shaft, and an outer portion of the one-way clutch. A power transmission device for a vehicle comprising an output side fulcrum provided on a member, and a connecting rod connecting the input side fulcrum and the output side fulcrum, between two one-way clutches adjacent in the axial direction, Two outer rings provided on the two outer members adjacent in the direction, one inner ring provided on an inner member fixed to the outer periphery of the output shaft, the two outer rings and A vehicular power comprising: a ball bearing having a plurality of balls in contact with the one inner ring; and a diameter of an outer peripheral surface of the inner ring in contact with the ball increasing from an axial center to an outer side. A transmission device is proposed.

  According to the invention described in claim 2, in addition to the configuration of claim 1, the plurality of power transmission units include at least first to third power transmission units adjacent in order in the axial direction, A vehicle power transmission device is proposed in which the one-way clutch is engaged in the order of 1 power transmission unit → the third power transmission unit → the second power transmission unit.

  The eccentric disk 18 of the embodiment corresponds to the input side fulcrum of the present invention, the pin 19c of the embodiment corresponds to the output side fulcrum of the present invention, and the engine E of the embodiment serves as the drive source of the present invention. Correspond.

  According to the configuration of the first aspect, the plurality of power transmission units of the vehicle power transmission device include an input side fulcrum that is variable in eccentricity from the axis of the input shaft and rotates together with the input shaft, and an outer portion of the one-way clutch. The output side fulcrum provided on the member is connected by a connecting rod, and the inner member of the one-way clutch is fixed to the output shaft, so when the input shaft rotates and the connecting rod reciprocates, the one-way clutch is intermittently engaged. Thus, the driving force is transmitted by intermittently rotating the output shaft. At that time, the output shaft can be continuously rotated by transmitting the driving force with a time difference by multiple power transmission units, and the eccentricity of the input side fulcrum is changed to increase or decrease the stroke of the reciprocating motion of the connecting rod. As a result, the rotation angle of the output shaft is increased or decreased to change the gear ratio.

  Between two axially adjacent one-way clutches, two outer rings provided on two axially adjacent outer members, one inner ring provided on an inner member fixed to the outer periphery of the output shaft, and two A ball bearing having two outer rings and a plurality of balls in contact with one inner ring, and the diameter of the outer peripheral surface of the inner ring in contact with the balls increases from the center in the axial direction toward the outside. Not only can the total number of parts of the bearing be reduced, but also the distance between two adjacent one-way clutches can be reduced to reduce the axial dimension of the vehicle power transmission device. In addition, when one of the two adjacent one-way clutches transmits driving force, even if the outer ring on one side of the one-way clutch expands due to a load, the shared ball moves along the outer circumferential surface of the inner ring. By moving to, it is possible to prevent a gap from being formed between the outer ring whose diameter has been enlarged and the ball, and to prevent generation of noise and deterioration of durability.

  According to the configuration of claim 2, the plurality of power transmission units include at least first to third power transmission units adjacent in order in the axial direction, the first power transmission unit → the third power transmission unit → the second power. Since the one-way clutch is engaged in the order of the transmission units, two adjacent power transmission units may not continuously transmit the driving force while all of the plurality of power transmission units transmit the driving force at least once. Always occurs. If the two adjacent power transmission units do not transmit the driving force continuously, the inner ring and the two outer rings sharing the ball do not receive the load from the ball at the same time. Occurrence and deterioration of durability can be avoided.

The skeleton figure of the power transmission device for vehicles. FIG. 2 is a detailed view of part 2 of FIG. 1. FIG. 3 is a sectional view taken along line 3-3 in FIG. 2 (TOP state). FIG. 3 is a sectional view taken along line 3-3 in FIG. 2 (LOW state). The action explanatory view in the TOP state. The action explanatory view in the LOW state. The disassembled perspective view of a one-way clutch. FIG. 8 is an enlarged view of part 8 in FIG. 2 (cross-sectional view taken along line 8-8 in FIG. 10). 9 is an enlarged view of 9 parts in FIG. FIG. 10 is a sectional view taken along line 10-10 in FIG. 8; Explanatory drawing of the operation | movement order of the three power transmission units juxtaposed in the axial direction. Explanatory drawing of the operation | movement order of six power transmission units juxtaposed in the axial direction.

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

  As shown in FIG. 1, the vehicle power transmission device for transmitting the driving force of the engine E to the drive wheels W, W via the left and right axles 10, 10 includes a crank type continuously variable transmission T and a differential gear D. Prepare.

  Next, the structure of the continuously variable transmission T will be described with reference to FIGS.

  As shown in FIGS. 2 and 3, the continuously variable transmission T of the present embodiment is obtained by superimposing a plurality (four in the embodiment) of power transmission units U... Having the same structure in the axial direction. These power transmission units U are provided with a common input shaft 11 and a common output shaft 12 arranged in parallel, and the rotation of the input shaft 11 is decelerated or increased and transmitted to the output shaft 12.

  Hereinafter, the structure of one power transmission unit U will be described as a representative. The input shaft 11 connected to the engine E and rotates passes through the hollow rotating shaft 14a of the speed change actuator 14 such as an electric motor so as to be relatively rotatable. The rotor 14b of the speed change actuator 14 is fixed to the rotating shaft 14a, and the stator 14c is fixed to the casing. The rotation shaft 14 a of the speed change actuator 14 can rotate at the same speed as the input shaft 11 and can rotate relative to the input shaft 11 at a different speed.

  A first pinion 15 is fixed to the input shaft 11 passing through the rotation shaft 14 a of the speed change actuator 14, and a crank-shaped carrier 16 is connected to the rotation shaft 14 a of the speed change actuator 14 so as to straddle the first pinion 15. The Two second pinions 17, 17 having the same diameter as the first pinion 15 are supported via pinion pins 16 a, 16 a at positions forming an equilateral triangle in cooperation with the first pinion 15, respectively. The first pinion 15 and the second pinions 17, 17 mesh with a ring gear 18 a formed eccentrically inside a disc-shaped eccentric disk 18. A ring portion 19 b provided at one end of the rod portion 19 a of the connecting rod 19 is fitted to the outer peripheral surface of the eccentric disk 18 via a ball bearing 20 so as to be relatively rotatable.

  A one-way clutch 21 provided on the outer periphery of the output shaft 12 is arranged inside the outer member 22 with a ring-shaped outer member 22 pivotally supported by a rod portion 19a of a connecting rod 19 via a pin 19c. 12, and an inner member 23 fixed to 12 and rollers 25 arranged in a wedge-shaped space formed between the outer member 22 and the inner member 23 and urged by engagement springs 24. The specific structure of the one-way clutch 21 will be described in detail later.

  As is clear from FIG. 2, the four power transmission units U... Share the crank-shaped carrier 16, but the phase of the eccentric disk 18 supported by the carrier 16 via the second pinions 17 and 17 is the same. Each power transmission unit U differs by 90 °. For example, in FIG. 2, the eccentric disk 18 of the leftmost power transmission unit U is displaced upward in the figure with respect to the input shaft 11, and the eccentric disk 18 of the third power transmission unit U from the left is relative to the input shaft 11. The eccentric discs 18 and 18 of the second and fourth power transmission units U and U from the left are located in the middle in the vertical direction.

  Next, the structure of the one-way clutch 21 will be described with reference to FIGS. 3 to 6, the one-way clutch 21 is schematically shown, and the actual structure is shown in FIGS.

  The one-way clutch 21 according to the present embodiment basically includes twelve rollers 25 between a circular inner peripheral surface 22a of an annular outer member 22 and an outer peripheral surface 23a bent in a wave shape of a cylindrical inner member 23. The connecting rod 19 is connected to the projecting portions 22b and 22b provided on the outer periphery of the outer member 22 via the pins 19c and the clips 40 and 40, and the output shaft is connected to the inner peripheral portion of the inner member 23. 12 are coupled so as not to rotate relative to each other.

  The one-way clutch 21 includes a cage 31 for supporting the engagement springs 24 that urge the rollers 25. The cage 31 includes a pair of annular members 32, 32 made of an annular plate material, and twelve spring support rods 33, which are arranged at equal intervals in the circumferential direction and connect the pair of annular portions 32, 32 to each other. The pair of annular members 32, 32 are disposed on both sides in the axial direction of the twelve rollers 25, and the twelve spring support rods 33 are disposed between the twelve rollers 25. The inner peripheral portion of the annular member 32 is formed in a corrugated shape, and the cage 31 is coupled to the inner member 23 so as not to be relatively rotatable by engaging with the corrugated outer peripheral surface 23 a of the inner member 23.

  The engagement spring 24 is formed by bending a single elastic plate with an S-shaped cross section, one end of which is fixed to the spring support rod 33 of the cage 31 by welding or the like, and the other end is an elastically deformable biasing portion. 24a is formed.

  One ball bearing 34 is disposed between two adjacent one-way clutches 21 and 21, and the ball bearings 34 allow the outer members 22, 22 and the inner member 23 to rotate relative to each other while maintaining a concentric state. Connected. The ball bearing 34 is formed by arranging a plurality of balls 37... Between two outer rings 35, 35 and one inner ring 36, and the two outer rings 35, 35 are mutually connected with two outer members 22, 22 adjacent in the axial direction. The inner ring 36 is formed as a separate member and is fixed to the outer peripheral surface 23 a of the inner member 23. That is, one ball bearing 34 supports the two outer rings 35, 35 with a common ball 37, so that the two outer members 22, 22 of the two adjacent one-way clutches 21, 21 are supported in a relatively rotatable manner. The

  An annular concave groove 36a (see FIG. 9) is formed on the outer peripheral surface of the inner ring 36 with which the balls 37 abut, and the diameter of the outer peripheral surface of the inner ring 36 increases from the axial center to the outer side. Also, annular concave grooves 35a (see FIG. 9) are formed at the corners of the respective outer rings 35 with which the balls 37 abut. The curvature radii of these three concave grooves 35a, 35a, 36a are set to be larger than the curvature radii of the balls 37, so that the balls 37 are in point contact with the outer rings 35, 35 and the inner ring 36 at three points.

  Further, an axial spring 38 is disposed between one side surface of the inner ring 36 of the ball bearing 34 and one annular member 32 of the cage 31, and a plurality of protrusions 38a projecting from the inner periphery of the axial spring 38 are annular. It passes between the recesses 32a on the inner periphery of the member 32 and elastically contacts the end face of the rollers 25. An annular ring spring 39 is disposed in an annular groove 22c formed in the inner peripheral surface 22a of the outer member 22, and this ring spring 39 abuts on the peripheral surface of the roller 25, so as to contact the outer peripheral surface 23a of the inner member 23. Energize towards.

  The two ball bearings 34 ′ and 34 ′ (see FIG. 8) located at both ends in the axial direction of the four one-way clutches 21 arranged side by side have one inner ring 36 and one outer ring 35. Only abut.

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

  First, the operation of one power transmission unit U of the continuously variable transmission T will be described. When the rotation shaft 14 a of the speed change actuator 14 is rotated relative to the input shaft 11, the carrier 16 rotates about the axis L <b> 1 of the input shaft 11. At this time, the center O of the carrier 16, that is, the center of the equilateral triangle formed by the first pinion 15 and the two second pinions 17, 17 rotates around the axis L 1 of the input shaft 11.

  3 and 5 show a state in which the center O of the carrier 16 is on the opposite side of the output shaft 12 with respect to the first pinion 15 (that is, the input shaft 11). The eccentricity is maximized and the ratio of the continuously variable transmission T is in the TOP state. 4 and 6 show a state in which the center O of the carrier 16 is on the same side as the output shaft 12 with respect to the first pinion 15 (that is, the input shaft 11). At this time, the eccentric disk 18 with respect to the input shaft 11 The amount of eccentricity is minimized and the ratio of the continuously variable transmission T is in the LOW state.

  In the TOP state shown in FIG. 5, when the input shaft 11 is rotated by the engine E and the rotation shaft 14 a of the speed change actuator 14 is rotated at the same speed as the input shaft 11, the input shaft 11, the rotation shaft 14 a, the carrier 16, With the one pinion 15, the two second pinions 17 and 17, and the eccentric disk 18 being integrated, the pinion 15 rotates eccentrically around the input shaft 11 (see arrow A). While rotating from FIG. 5A through FIG. 5B to the state of FIG. 5C, the ring portion 19b is supported on the outer periphery of the eccentric disk 18 via the ball bearing 20 so as to be relatively rotatable. The connecting rod 19 rotates the outer member 22 pivotally supported by a pin 19c at the tip of the rod portion 19a in the counterclockwise direction (see arrow B). 5A and 5C show both ends of rotation of the outer member 22 in the arrow B direction.

  When the outer member 22 rotates in the arrow B direction in this way, the rollers 25... Bite into the wedge-shaped space between the outer member 22 and the inner member 23 of the one-way clutch 21, and the rotation of the outer member 22 passes through the inner member 23. Therefore, the output shaft 12 rotates counterclockwise (see arrow C).

  When the input shaft 11 and the first pinion 15 further rotate, the eccentric disk 18 in which the ring gear 18a is engaged with the first pinion 15 and the second pinion 17, 17 rotates eccentrically in the counterclockwise direction (see arrow A). While rotating from the state shown in FIG. 5C to the state shown in FIG. 5A, the ring portion 19b is supported on the outer periphery of the eccentric disk 18 via the ball bearing 20 so as to be relatively rotatable. The connecting rod 19 rotates the outer member 22 pivotally supported by a pin 19c at the tip of the rod portion 19a in the clockwise direction (see arrow B ′). FIG. 5C and FIG. 5A show both ends of the rotation of the outer member 22 in the arrow B ′ direction.

  When the outer member 22 rotates in the direction of the arrow B ′ in this way, the rollers 25 are pushed out from the wedge-shaped space between the outer member 22 and the inner member 23 while compressing the engagement springs 24, thereby the outer member. 22 slips with respect to the inner member 23 and the output shaft 12 does not rotate.

  As described above, when the outer member 22 reciprocates, the output shaft 12 rotates counterclockwise (see arrow C) only when the rotation direction of the outer member 22 is counterclockwise (see arrow B). The shaft 12 rotates intermittently.

  FIG. 6 shows the operation when the continuously variable transmission T is operated in the LOW state. At this time, since the position of the input shaft 11 coincides with the center of the eccentric disk 18, the eccentric amount of the eccentric disk 18 with respect to the input shaft 11 becomes zero. In this state, when the input shaft 11 is rotated by the engine E and the rotating shaft 14a of the speed change actuator 14 is rotated at the same speed as the input shaft 11, the input shaft 11, the rotating shaft 14a, the carrier 16, the first pinion 15, 2 In a state where the second pinions 17 and 17 and the eccentric disk 18 are integrated, the input pin 11 is rotated eccentrically in the counterclockwise direction (see arrow A). However, since the eccentric amount of the eccentric disk 18 is zero, the stroke of the reciprocating motion of the connecting rod 19 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 carrier 16 is set between the TOP state of FIG. 3 and the LOW state of FIG. 4, operation at an arbitrary ratio between the zero ratio and the predetermined ratio becomes possible.

  In the continuously variable transmission T, the phases of the eccentric disks 18 of the four power transmission units U arranged in parallel are shifted by 90 ° from each other, so that the four power transmission units U are alternately driven. By transmitting, that is, any one of the four one-way clutches 21 is always in an engaged state, the output shaft 12 can be continuously rotated.

  Next, the operation of the ball bearing 34 of the one-way clutch 21 will be described.

  In FIG. 9, outer members 22 and 22 of two adjacent one-way clutches 21 and 21 swing at different phases by connecting rods 19 and 19 connected thereto. For example, when the right outer member 22 in the figure swings in one direction and the one-way clutch 21 is engaged, the rollers 25 are wedge-shaped spaces between the outer peripheral surface 23a of the inner member 23 and the inner peripheral surface 22a of the outer member 22. , The outer member 22 receives a radially outward load from the rollers 25 and expands in the direction of arrow A, and a gap is generated between the concave groove 35a of the outer ring 35 and the ball 37. At this time, if the outer member 22 on the left side in the drawing swings in the other direction and the one-way clutch 21 is not engaged, the outer member 22 does not receive a radially outward load from the rollers 25. There is no diameter.

  As a result, the balls 37... Move along the concave groove 36a of the inner ring 36 from the solid line position to the chain line position in the direction of arrow B, and the contact state with the concave groove 35a of the right outer ring 35 whose diameter has been expanded is maintained. . In this way, even if one of the two outer rings 35, 35 is expanded in diameter by a load due to engagement of the one-way clutch 21, the balls 37 disposed between the two outer rings 35, 35 follow the expanded outer ring 35. The movement of the balls 37 prevents the balls 37 from rattling, so that it is possible to avoid a decrease in durability due to noise generation or abnormal wear. In addition, since one ball bearing 34 is shared by the two one-way clutches 21 and 21 arranged on both sides in the axial direction, not only the number of parts can be reduced, but also the interval between the two adjacent one-way clutches 21 and 21 is reduced. Thus, the axial dimension of the continuously variable transmission T can be reduced.

  By the way, when the two one-way clutches 21 and 21 adjacent in the axial direction are both engaged, both the two outer rings 35 and 35 in FIG. 9 are expanded in diameter, and the ball 37. Therefore, it is desirable to shift the timing at which the two one-way clutches 21 and 21 adjacent in the axial direction are engaged as much as possible. When the continuously variable transmission T includes four power transmission units U, each time the phase of the input shaft 11 changes by 90 °, the four one-way clutches 21. The engagement order may be set so that the one-way clutches 21 and 21 are not continuously engaged.

  FIG. 11 shows a state in which arbitrary three power transmission units U... Arranged continuously in the axial direction are taken out of the plurality of power transmission units U of the continuously variable transmission T. Assuming that the three power transmission units U are # 1, # 2, and # 3, the three power transmission units U are engaged so that the one-way clutches 21 are engaged in the order of # 1, # 3, and # 2. If the phases of the eccentric disks 18 are set, it is possible to avoid a situation in which the one-way clutches 21 of the adjacent power transmission units U are continuously engaged.

  FIG. 12 shows a case where the continuously variable transmission T includes six power transmission units U... # 1 to # 6, and the one-way clutch 21 is # 1 → # 6 → # 2 → # 4 →. Engage in the order of # 3 → # 5. In this case, only the adjacent one-way clutches 21 and 21 of the power transmission units U and U of # 3 and # 4 are continuously engaged, but the other adjacent one-way clutches 21 are continuously engaged. Therefore, rattling of the balls 37 of the ball bearing 34 can be minimized.

  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, the continuously variable transmission T according to the embodiment includes four power transmission units U, but the number of power transmission units U is not limited to four.

  In the embodiment, a part of the outer member 22 of the one-way clutch 21 is used as the outer ring 35 of the ball bearing 34. However, the outer ring 35 may be configured as a separate member and fixed to the outer member 22.

  In the embodiment, the inner ring 36 of the ball bearing 34 is configured as a separate member from the inner member 23 of the one-way clutch 21, but a part of the inner member 23 may be used as the inner ring 36.

11 Input shaft 12 Output shaft 18 Eccentric disc (input side fulcrum)
19 Connecting rod 19c Pin (Output side fulcrum)
21 One-way clutch 22 Outer member 23 Inner member 34 Ball bearing 35 Outer ring 36 Inner ring 37 Ball E Engine (drive source)
U Power transmission unit

Claims (2)

A plurality of power transmission units (U) for shifting the rotation of the input shaft (11) connected to the drive source (E) and transmitting it to the output shaft (12) are juxtaposed in the axial direction,
Each of the power transmission units (U) has an input side fulcrum (18) that is variable in eccentricity from the axis of the input shaft (11) and rotates together with the input shaft (11), and the output shaft (12). ) Connected to the one-way clutch (21), the output side fulcrum (19c) provided on the outer member (22) of the one-way clutch (21), the input side fulcrum (18) and the output side fulcrum (19c). A vehicle power transmission device comprising a connecting rod (19) for connecting
Between the two one-way clutches (21) adjacent in the axial direction, there are two outer rings (35) provided on the two outer members (22) adjacent in the axial direction and the outer periphery of the output shaft (12). A ball bearing having one inner ring (36) provided on the inner member (23) fixed to the inner member (23), and the two outer rings (35) and a plurality of balls (37) in contact with the one inner ring (36). 34), and the diameter of the outer peripheral surface of the inner ring (36) with which the ball (37) abuts increases from the center in the axial direction toward the outside.   The plurality of power transmission units (U) include at least first to third power transmission units adjacent in order in the axial direction, and the first power transmission unit → the third power transmission unit → the second power transmission unit. The vehicle power transmission device according to claim 1, wherein the one-way clutch (21) is engaged in order.

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