JP2015209899A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a continuously variable transmission that can dispense with a drive source dedicated to an output deceleration mechanism.SOLUTION: A continuously variable transmission 1 comprises: a crank mechanism 20 converting a rotational motion of a rotary disc 6 to an oscillation motion of an oscillation link 18; a first one-way clutch 17; a rotation radius adjustment mechanism 4; and an output deceleration mechanism 100. The output deceleration mechanism 100 includes a first pulley 101 provided on an input shaft 2; a second pulley 102 provided on an output shaft 3; a band body 103 that can transmit power between the first pulley 101 and the second pulley 102; and a differential mechanism that includes three or first to third rotation elements. In the differential mechanism, a pinion 70 is coupled to the first rotation element, the second shaft 2 is coupled to a second rotation element, an abutment portion is provided on a third rotation element to abut on a cam surface provided on a side surface of the first pulley 101, and a width of the first pulley 101 is changed by the cam surface depending on a change in relative phases of the pinion 70 and the input shaft 2.

Description

  The present invention relates to a continuously variable transmission including a motion conversion mechanism that converts rotational motion into swing motion.

  Conventionally, an input shaft to which driving force from a driving source such as an engine provided in a vehicle is transmitted, an output shaft arranged in parallel with the input shaft, and a plurality of turning radius adjustment mechanisms provided on the input shaft, A plurality of oscillating links that are pivotally supported by the output shaft, an input side annular portion that is rotatably fitted to the rotation radius adjusting mechanism at one end, and the other end is oscillated. A four-bar link mechanism type continuously variable transmission is known that includes a connecting rod connected to a rocking end of a link (see, for example, Patent Document 1).

  In Patent Document 1, each turning radius adjusting mechanism includes a disc-shaped cam portion provided eccentrically with respect to the rotation center axis of the input shaft, and a rotating portion provided eccentrically on the cam portion and rotatably provided. And a pinion shaft provided integrally with a plurality of pinions in the axial direction. A first one-way clutch is provided between the swing link and the output shaft. The first one-way clutch fixes the swing link to the output shaft when the swing link is about to rotate relative to the output shaft, and On the other hand, the swing link is idled.

  The cam part connection body is hollow by connecting through holes of the cam parts, and a pinion shaft is inserted into the inside. The inserted pinion shaft is exposed from the notch hole of each cam portion. The rotating part is provided with a receiving hole for receiving the camshaft. Internal teeth are formed on the inner peripheral surface of the rotating part that forms the receiving hole.

  The internal teeth mesh with the pinion shaft exposed from the notch hole of the camshaft. When the input shaft and the pinion shaft are rotated at the same speed, the radius of rotational motion on the input shaft side of the rotational radius adjusting mechanism is maintained. When the rotational speeds of the input shaft and the pinion shaft are made different, the radius of the rotational motion on the input shaft side of the rotational radius adjusting mechanism is changed, and the gear ratio is changed.

  When the rotation radius adjustment mechanism is rotated by rotating the input shaft, the input-side annular portion of the connecting rod rotates, and the swing end of the swing link connected to the other end of the connecting rod swings. Move. That is, a lever crank mechanism (motion conversion mechanism) is configured by the turning radius adjusting mechanism, the connecting rod, and the swing link. Since the swing link is provided on the output shaft via the first one-way clutch, the rotational drive force (torque) is transmitted to the output shaft only when rotating to one side.

  The eccentric direction of the cam portion of each turning radius adjusting mechanism is set so as to make a round around the input shaft with different phases. Therefore, the connecting rod that is externally fitted to each turning radius adjusting mechanism causes the swing link to transmit torque to the output shaft in order, so that the output shaft can be smoothly rotated.

  Further, in the four-bar linkage type continuously variable transmission configured as described above, engine braking is not possible. Moreover, the driving source for driving is rotated using the rotational force of the driving wheel, and for example, fuel consumption cannot be improved by fuel cut or regeneration using the electric motor as a generator cannot be performed. For this reason, what is equipped with the output deceleration mechanism which has a 2nd one-way clutch for using an engine brake or turning a driving source for driving using the rotational force of a driving wheel is also known (for example, Patent Document 2).

JP-T-2005-502543 International Publication No. 2012/026181

  In a conventional continuously variable transmission, a drive source dedicated to the output speed reduction mechanism is provided in order to switch the operation or stop of the output speed reduction mechanism. For this reason, there is a risk that the continuously variable transmission will be increased in size by the amount of the drive source dedicated to the output speed reduction mechanism, and the manufacturing cost may increase.

  In view of the above, an object of the present invention is to provide a continuously variable transmission that does not require a drive source dedicated to an output speed reduction mechanism.

[1] In order to achieve the above object, the present invention provides:
An input shaft to which the driving force of the driving source for traveling is transmitted;
An output shaft provided parallel to the input shaft;
A motion converting mechanism that has a rotating portion that rotates together with the input shaft and a swinging portion provided on the output shaft, and that converts the rotational motion of the rotating portion into the swinging motion of the swinging portion;
The swinging portion is fixed to the output shaft when the swinging portion is about to rotate relative to the output shaft, and the swinging portion is relatively positioned relative to the output shaft. A one-way rotation prevention mechanism that idles the rocking portion with respect to the output shaft when attempting to rotate;
A rotation radius adjusting mechanism having a pinion to which the driving force of the adjustment drive source is transmitted, and capable of adjusting the rotation radius of the rotating portion by adjusting a relative phase between the pinion and the input shaft;
An output speed reduction mechanism capable of decelerating the rotational speed of the output shaft using the driving force of the input shaft;
A continuously variable transmission that changes a gear ratio by changing a rotation radius of a rotating part,
The output deceleration mechanism is
A first pulley provided on the input shaft;
A second pulley provided on the output shaft;
A belt-like body wound around the first pulley and the second pulley and capable of transmitting power between the first pulley and the second pulley;
A differential mechanism comprising first to third three rotating elements;
Connecting the pinion to the first rotating element;
Connecting the input shaft to the second rotating element;
The third rotating element is provided with a contact portion that contacts a cam surface provided on a side surface of the first pulley,
A width of the first pulley is changed by the cam surface by a change in a relative phase between the pinion and the input shaft.

  According to the present invention, the operation or stop of the output speed reduction mechanism can be switched by adjusting the rotation radius by the adjustment drive source. Therefore, a compact continuously variable transmission that does not require a drive source dedicated to the output speed reduction mechanism can be manufactured.

  [2] In the present invention, the first pulley is provided with a maximum side locking portion that locks the contact portion with the first pulley when the rotation radius of the rotating portion is maximum, and the differential mechanism Is preferably configured so that the rotation direction in which the contact portion is locked to the maximum-side locking portion is the reverse rotation direction that is the rotation direction when the vehicle travels backward.

  According to such a configuration, the vehicle can travel backward using the driving force of the adjusting drive source.

  [3] In the present invention, the first pulley is provided with a minimum-side locking portion that locks the contact portion with the first pulley when the rotation radius of the rotating portion is minimum, and the differential mechanism Is preferably configured such that the rotation direction in which the contact portion is locked to the minimum-side locking portion is the forward rotation direction that is the rotation direction when the vehicle travels forward. According to such a configuration, for example, when the rotation radius is equal to or less than a predetermined radius, such as when the rotation radius of the rotation unit is “0”, the travel drive source can be started using the drive force of the adjustment drive source. .

  [4] In the present invention, a flat portion is provided in a portion where the rotation radius of the rotation portion of the cam surface is the smallest, and when the rotation radius is equal to or less than a predetermined value due to the flat portion, the first portion is provided. It is preferable that the pulley is configured to be constant without widening. According to this configuration, it is possible to set an infinite ratio in which the transmission ratio is infinite and the output shaft rotation is “0”.

Explanatory drawing which shows typically embodiment of the continuously variable transmission of this invention. Explanatory drawing which shows the continuously variable transmission of this embodiment. Explanatory drawing which shows the motion conversion mechanism of this embodiment. Explanatory drawing which shows the change of the rotation radius of the rotation part of this embodiment. Explanatory drawing which shows the change of the rocking | fluctuation range of the rocking | swiveling part with respect to the change of the rotation radius of this embodiment. Explanatory drawing which shows the deceleration mechanism of the drive source for adjustment of this embodiment. The speed diagram which shows the rotational speed of the rotation element of the deceleration mechanism when the continuously variable transmission of this embodiment is shifting. The speed diagram which shows the rotational speed of the rotation element of the deceleration mechanism when the continuously variable transmission of this embodiment is maintaining the gear ratio constant. Explanatory drawing which shows the differential mechanism of this embodiment. Explanatory drawing which shows the contact part of this embodiment. FIG. 11A is an explanatory view showing a cam surface of the present embodiment. FIG. 11B is a cross-sectional view illustrating a state in which a side surface portion provided with a cam surface of the first pulley of the present embodiment is developed. The graph which shows the change of the rotation radius R1 of this embodiment, and the change of the rotation angle of a pinion. The speed diagram which shows the rotational speed of each rotation element of the state which is reducing the gear ratio of this embodiment and is shifting to the high speed side. FIG. 14 is a velocity diagram illustrating an enlarged part of the rotating element in FIG. 13. The speed diagram which shows the rotational speed of each rotation element in the state which is increasing the gear ratio of this embodiment and is shifting to the low speed side. The speed diagram which expands and shows the part of the rotation element of FIG. The speed diagram which shows the rotational speed of each rotation element of the state which is maintaining the gear ratio of this embodiment constant.

  A continuously variable transmission according to an embodiment of the present invention includes a motion conversion mechanism including a four-bar linkage mechanism, and a transmission gear ratio h (h = rotational speed of an input shaft / rotational speed of an output shaft) is set to infinity (∞). It is a kind of transmission that can make the rotation speed of the output shaft "0", so-called IVT (Infinity Variable Transmission).

  Referring to FIGS. 1 and 2, a continuously variable transmission 1 of a four-bar linkage mechanism type receives a rotational driving force from a traveling drive source ENG such as an engine or an electric motor that is an internal combustion engine, whereby a rotation center axis P1 is obtained. An output shaft 3 that is arranged in parallel to the rotation center axis P1 and that transmits rotational power to the drive wheels (not shown) of the vehicle via the differential gear DF, and the rotation center axis P1. And six turning radius adjusting mechanisms 4 provided on the head. A propeller shaft may be provided instead of the differential gear DF.

  As shown in FIG. 2, each turning radius adjusting mechanism 4 includes a cam disk 5 as a cam part and a rotating disk 6 as a rotating part. The cam disks 5 have a disk shape, are eccentric from the rotation center axis P <b> 1, and are provided in each rotation radius adjustment mechanism 4 so as to form one set with respect to one rotation radius adjustment mechanism 4. . The cam disk 5 is provided with a through hole 5a penetrating in the direction of the rotation center axis P1. Further, the cam disk 5 is opened in a direction opposite to the direction decentered with respect to the rotation center axis P1, and a notch hole 5b for communicating the outer peripheral surface of the cam disk 5 with the inner peripheral surface constituting the through hole 5a. Is provided.

  Each set of cam disks 5 is arranged so as to make a round in the circumferential direction of the rotation center axis P <b> 1 with six sets of cam disks 5 with a phase difference of 60 degrees.

  The cam disk 5 is formed integrally with the cam disk 5 of the adjacent turning radius adjusting mechanism 4 to constitute an integrated cam portion 5c. The integrated cam portion 5c may be formed by integral molding, or may be integrated by welding two cam portions. A pair of cam disks 5 of each turning radius adjusting mechanism 4 are fixed by bolts (not shown). The cam disk 5 located closest to the driving source for traveling on the rotation center axis P1 is formed integrally with the input end 2a. In this way, the input shaft 2 (camshaft) is configured by the input end 2a and the cam disk 5.

  The input shaft 2 (camshaft) includes an insertion hole 60 formed by connecting the through holes 5 a of the cam disk 5. Thereby, the input shaft 2 (camshaft) is formed in a hollow shaft shape in which one end opposite to the traveling drive source ENG is open and the other end is closed. As a method for integrally forming the cam disk 5 and the input end 2a, integral molding may be used, or the cam disk 5 and the input end 2a may be integrated by welding.

  Each set of cam disks 5 is rotatably fitted with a disk-shaped rotating disk 6 having a receiving hole 6a for receiving the cam disk 5 in an eccentric state.

  As shown in FIG. 3, the rotary disk 6 has a center point of the cam disk 5 as P2, a center point of the rotary disk 6 as P3, a distance La between the rotation center axis P1 and the center point P2, and the center point P2 and the center point. It is eccentric with respect to the cam disk 5 so that the distance Lb of P3 is the same.

  The receiving hole 6 a of the rotating disk 6 is provided with internal teeth 6 b that are positioned between the pair of cam disks 5.

  In the insertion hole 60 of the input shaft 2, the pinion 70 is positioned so as to be concentric with the rotation center axis P <b> 1 and corresponding to the inner teeth 6 b of the rotating disk 6, and the pinion 70 is rotatable relative to the input shaft 2 (cam shaft). It is arranged to become. The pinion 70 is formed integrally with the pinion shaft 72. The pinion 70 may be configured separately from the pinion shaft 72, and the pinion 70 may be connected to the pinion shaft 72 by spline coupling. In the present embodiment, the term “pinion 70” is defined as including the pinion shaft 72.

  The pinion 70 meshes with the internal teeth 6 b of the rotating disk 6 through the notch hole 5 b of the cam disk 5. The pinion shaft 72 is provided with a bearing 74 positioned between the adjacent pinions 70. The pinion shaft 72 supports the input shaft 2 (camshaft) via the bearing 74. The speed reduction mechanism 8 is connected to the pinion shaft 72. The driving force of the adjusting drive source 14 is transmitted to the pinion 70 via the speed reduction mechanism 8.

  As shown in FIG. 6, the speed reduction mechanism 8 is constituted by a planetary gear mechanism.

  As shown in FIG. 3, the rotating disk 6 is eccentric with respect to the cam disk 5 such that the distance La and the distance Lb are the same, and therefore the center point P3 of the rotating disk 6 is the same as the rotation center axis P1. The distance between the rotation center axis P1 and the center point P3, that is, the eccentric amount R1 can be set to “0” so as to be positioned on the axis.

  On the periphery of the rotating disk 6, a connecting rod 15 is provided with an input-side annular portion 15a having a large diameter at one end and an output-side annular portion 15b having a smaller diameter than the diameter of the input-side annular portion 15a at the other end. The input-side annular portion 15a is rotatably fitted via a connecting rod bearing 16 composed of a roller bearing. In addition, the connecting rod bearing 16 may comprise two ball bearings arranged in the axial direction as a set. The output shaft 3 is provided with six swing links 18 corresponding to the connecting rod 15 via the first one-way clutch 17.

  The first one-way clutch 17 is provided between the swing link 18 and the output shaft 3, and when the swing link 18 is about to rotate relative to the output shaft 3 on one side, the swing link 18 is connected to the output shaft. The swing link 18 is idled with respect to the output shaft 3 when it is fixed to 3 and tries to rotate relative to the other side.

  The swing link 18 is formed in an annular shape, and a swing end portion 18 a connected to the output-side annular portion 15 b of the connecting rod 15 is provided below the swing link 18. The swing end portion 18a is provided with a pair of protruding pieces 18b protruding so as to sandwich the output-side annular portion 15b in the axial direction. The pair of projecting pieces 18b are provided with insertion holes 18c corresponding to the inner diameter of the output-side annular portion 15b. A connecting pin 19 is inserted into the insertion hole 18c and the output side annular portion 15b. Thereby, the connecting rod 15 and the swing link 18 are connected.

  In the present embodiment, the oscillating end 18a is disposed below the output shaft 3 so that the oscillating end 18a of the oscillating link 18 is immersed in the oil reservoir of lubricating oil collected below the case 80. Has been. As a result, the oscillating end 18a can be lubricated with the oil reservoir, and the lubricating oil in the oil reservoir can be lifted by the oscillating motion of the oscillating link 18 to lubricate other components of the continuously variable transmission 1. it can.

  In the description of the embodiment, the gear ratio is defined as the rotational speed of the input shaft / the rotational speed of the output shaft.

  FIG. 4 shows the positional relationship between the pinion shaft 72 and the rotating disk 6 in a state where the eccentric amount R1 as the rotating radius of the rotating disk 6 of the rotating radius adjusting mechanism 4 is changed. FIG. 4A shows a state in which the amount of eccentricity R1 is “maximum”, and the pinion shaft is such that the rotation center axis P1, the center point P2 of the cam disk 5, and the center point P3 of the rotation disk 6 are aligned. 72 and the rotary disk 6 are located. At this time, the gear ratio h is minimized.

  4B shows a state in which the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 4A, and FIG. 4C shows a state in which the eccentric amount R1 is set to “small” which is further smaller than that in FIG. 4B. The gear ratio h is “medium” which is larger than the gear ratio h in FIG. 4A in FIG. 4B, and “large” which is larger than the gear ratio h in FIG. 4B in FIG.

  FIG. 4D shows a state where the amount of eccentricity R1 is “0”, and the rotation center axis P1 and the center point P3 of the rotating disk 6 are located concentrically. The gear ratio h at this time is infinite (∞). In the continuously variable transmission 1 of the first embodiment, the radius of rotational motion on the input shaft 2 side can be adjusted by changing the amount of eccentricity R1 by the rotational radius adjusting mechanism 4.

  FIG. 5 shows a change in the swing range of the swing link 18 when the eccentric amount R1 (rotation radius) of the turning radius adjusting mechanism 4 is changed. 5A shows the swing range of the swing link 18 when the eccentric amount R1 is the maximum, FIG. 5B shows the swing range of the swing link 18 when the eccentric amount R1 is medium, and FIG. The swing range of the swing link 18 when the eccentric amount R1 is small is shown. It can be seen from FIG. 5 that the swing range becomes narrower as the eccentric amount R1 becomes smaller. When the eccentric amount R1 becomes “0”, the swing link 18 does not swing.

  In the present embodiment, the turning radius adjusting mechanism 4, the connecting rod 15, and the swing link 18 constitute a lever crank mechanism 20 (four-bar linkage mechanism). Then, the lever crank mechanism 20 converts the rotational motion of the input shaft 2 into the swing motion of the swing link 18. The continuously variable transmission 1 of this embodiment includes a total of six lever crank mechanisms 20.

  When the input shaft 2 is rotated and the pinion shaft 72 is rotated at the same speed as the input shaft 2 when the eccentric amount R1 is not “0”, each connecting rod 15 changes its phase by 60 degrees, and the eccentric amount R1. On the basis of this, it is repeatedly swung between the input shaft 2 and the output shaft 3 by alternately pushing to the output shaft 3 side or pulling to the input shaft 2 side.

  Since the output side annular portion 15b of the connecting rod 15 is connected to the swing link 18 provided on the output shaft 3 via the first one-way clutch 17, the swing link 18 is pushed and pulled by the connecting rod 15. When swinging, the output shaft 3 rotates only when the swing link 18 rotates in either the pushing direction side or the pulling direction side, and when the swing link 18 rotates in the other direction, output is performed. The force of the oscillating motion of the oscillating link 18 is not transmitted to the shaft 3, and the oscillating link 18 rotates idle. Since each turning radius adjusting mechanism 4 is arranged with a phase changed every 60 degrees, the output shaft 3 is rotated in turn by each turning radius adjusting mechanism 4.

  Further, the continuously variable transmission 1 of the present embodiment includes a control unit ECU that controls the adjustment drive source 14. The control unit ECU is an electronic unit composed of a CPU, a memory, and the like, and controls the adjustment drive source 14 by executing a control program held in the memory by the CPU, so that the eccentricity of the turning radius adjustment mechanism 4 is controlled. Serves to regulate the amount R1.

  As shown in the skeleton diagram in FIG. 6, the speed reduction mechanism 8 includes first to third planetary gear mechanisms PGS1 to PGS3. The first planetary gear mechanism PGS1 is configured as a single pinion type including a sun gear Sa, a ring gear Ra, and a carrier Ca that rotatably supports a planetary gear Pa that meshes with the sun gear Sa and the ring gear Ra.

  The upper part of FIG. 7 shows a collinear diagram that can represent the rotational speeds of the three single elements of the sun gear Sa, the carrier Ca, and the ring gear Ra of the first planetary gear mechanism PGS1 with straight lines. The three single elements of the first planetary gear mechanism PGS1 are arranged from one side in the alignment order in the collinear diagram, and in this embodiment, in order from the right side of FIG. 8, the first single element, the second single element, and the third single element Then, the first single element is the sun gear Sa, the second single element is the carrier Ca, and the third single element is the ring gear Ra.

  In the nomograph, the gear ratio of the first planetary gear mechanism PGS1 (the number of teeth of the ring gear / the number of teeth of the sun gear) is i, and between the sun gear Sa (first single element) and the carrier Ca (second single element). The ratio between the distance and the distance between the carrier Ca (second single element) and the ring gear Ra (third single element) is set to be i: 1. In the present embodiment, the gear ratio i of the first planetary gear mechanism PGS1 is set to 2.00. 7 and 8, the horizontal line at the lower end indicates that the rotational speed is “0”, and the broken line is the same as the rotational speed of the input shaft 2 to which the power of the traveling drive source is transmitted. “N1”.

  The second planetary gear mechanism PGS2 is configured as a single pinion type including a sun gear Sb, a ring gear Rb, and a carrier Cb that pivotally supports a planetary gear Pb that meshes with the sun gear Sb and the ring gear Rb.

  The collinear diagram that can represent the rotational speeds of the three single elements of the sun gear Sb, the carrier Cb, and the ring gear Rb of the second planetary gear mechanism PGS2 in the middle of FIG. The three single elements of the second planetary gear mechanism PGS2 are arranged from one side in the alignment order in the collinear diagram, and in the present embodiment, in order from the right side in FIG. 7, the fourth single element, the fifth single element, and the sixth single element Then, the fourth single element is the sun gear Sb, the fifth single element is the carrier Cb, and the sixth single element is the ring gear Rb.

  In the collinear diagram, j is the gear ratio of the second planetary gear mechanism PGS2 (the number of teeth of the ring gear / the number of teeth of the sun gear), and between the sun gear Sb (fourth single element) and the carrier Cb (fifth single element). The ratio between the distance and the distance between the carrier Cb (fifth single element) and the ring gear Rb (sixth single element) is set to be j: 1. In the present embodiment, the gear ratio j of the second planetary gear mechanism PGS2 is set to 2.00.

  The third planetary gear mechanism PGS3 includes a sun gear Sc, a ring gear Rc, and a carrier that pivotally supports a stepped planetary gear Pc in which the large-diameter portion Pc1 meshes with the sun gear Sc and the small-diameter portion Pc2 meshes with the ring gear Rc. It is comprised by the single pinion type | mold which consists of Cc.

  The lower part of FIG. 7 shows a collinear diagram in which the rotation speeds of the three single elements of the sun gear Sc, the carrier Cc, and the ring gear Rc of the third planetary gear mechanism PGS3 can be represented by straight lines. Three single element elements of the third planetary gear mechanism PGS3 are arranged from one side in the alignment order in the collinear diagram, and in this embodiment, in order from the right side of FIG. 7, the seventh single element, the eighth single element, the ninth single element and Then, the seventh single element is the sun gear Sc, the eighth single element is the carrier Cc, and the ninth single element is the ring gear Rc.

  In the nomograph, the gear ratio of the third planetary gear mechanism PGS3 ((the number of teeth of the ring gear / the number of teeth of the sun gear) × (the number of teeth of the large diameter portion Pc1 of the stepped planetary gear Pc / the number of teeth of the small diameter portion Pc2)). k, a distance between the sun gear Sc (seventh single element) and the carrier Cc (eight single element), and a distance between the carrier Cc (eight single element) and the ring gear Rc (ninth single element) Is set to be k: 1.

  The gear ratio k of the third planetary gear mechanism PGS3 is connected to the pinion 70 when the sun gear Sa (first single element) of the first planetary gear mechanism PGS1 is rotated using the driving force of the adjusting drive source 14. The rotation speed of the carrier Cc (eight single element) of the third planetary gear mechanism PGS3 is appropriately set so as to be a desired rotation speed with respect to the rotation speed of the sun gear Sa (first single element).

  The carrier Ca (second single element) is connected to the carrier Cb (fifth single element), and the carrier Ca (second single element) and the carrier Cb (fifth single element) constitute the first connected body Ca-Cb. The The ring gear Ra (third single element) is connected to the ring gear Rc (9th single element), and the ring gear Ra (third single element) and the ring gear Rc (9th single element) constitute a second connected body Ra-Rc. The The ring gear Rb (sixth single element) is coupled to the sun gear Sc (seventh single element), and the ring gear Rb (sixth single element) and the sun gear Sc (seventh single element) constitute the third coupling body Rb-Sc. The

  The second coupling body Ra-Rc is a first input element to which power from the travel drive source is transmitted via the input shaft 2 constituted by the input end 2a and the cam disk 5. The sun gear Sa (the first single element) includes a first intermediate gear G1a in which the driving force of the adjusting drive source 14 meshes with an adjusting pinion 14a provided on the rotating shaft of the adjusting drive source 14, and the first gear G1a. It is transmitted via a first gear train G1 comprising a second intermediate gear G1b meshing with the intermediate gear G1a. Accordingly, the sun gear Sa (first single element) is a second input element to which the driving force of the adjustment drive source 14 is transmitted via the first gear train G1. The carrier Cc (eighth single element) is a transmission element coupled to the pinion 70 serving as a transmission unit. The first gear train G1 may be omitted, and the driving force of the adjustment drive source 14 may be transmitted directly to the sun gear Sa (first single element).

  The sun gear Sb (fourth single element) is provided with a brake B1 as a fixing mechanism. The brake B1 fixes the sun gear Sb (fourth single element) to the case 80 such as the continuously variable transmission 1, the speed reduction mechanism 8, the adjustment drive source 14, and the like, and a release state for releasing the fixation. It is configured to be switchable between states. In the present embodiment, the brake B1 is always fixed. Therefore, the brake B1 may be omitted and the sun gear Sb (fourth single element) may be directly fixed to the case 80.

  When the rotational speed of the input shaft 2 connected to the input shaft 2 and the rotational speed of the pinion shaft 72 are the same, the rotating disk 6 rotates together with the cam disk 5. When there is a difference between the rotational speed of the input shaft 2 and the rotational speed of the pinion shaft 72, the rotating disk 6 rotates the periphery of the cam disk 5 around the center point P <b> 2 of the cam disk 5.

  As shown in FIG. 3, the rotating disk 6 is eccentric with respect to the cam disk 5 such that the distance La and the distance Lb are the same, and therefore the center point P3 of the rotating disk 6 is the same as the rotation center axis P1. The distance between the rotation center axis P1 and the center point P3, that is, the eccentric amount R1 can be set to “0” so as to be positioned on the axis.

  FIG. 8 shows an alignment chart in a state in which the speed ratio h is maintained constant. In the collinear diagram of the third planetary gear mechanism PGS3 shown in the lower part of FIG. 8, the rotational speed of the second connecting body Ra-Rc connected to the input shaft 2 is the third planetary gear mechanism to which the pinion 70 is connected. When the rotation speed of the carrier Cc (eighth single element) of the PGS3 is “N1”, that is, when the speed ratio h is kept constant, the first planetary gear mechanism PGS1 shown in the upper part of FIG. In the nomogram, it can be seen that the rotational speed of the sun gear Sa of the first planetary gear mechanism PGS1 to which the adjusting drive source 14 is connected is “0”.

  Therefore, according to the continuously variable transmission 1 of the present embodiment, when the gear ratio h is constant, the sun gear Sa (first single element) as the second input element to which the driving force of the adjusting drive source 14 is transmitted. It turns out that it is not necessary to rotate, and it should just control so that the rotation speed of the sun gear Sa (1st single element) which is a 2nd input element may be set to "0". The collinear diagram of FIG. 7 shows a state where the gear ratio h is changed.

  Further, the continuously variable transmission 1 of the present embodiment uses the rotational load of the driving source ENG for traveling to apply the engine brake to reduce the rotational speed of the output shaft 3 or to reduce the rotational force of the drive wheels. An output speed reduction mechanism 100 is provided for turning the driving source for use. In the case where the traveling drive source is configured by an electric motor, an output speed reduction mechanism can be used so as to perform regeneration using the electric motor as a generator.

  As shown in FIG. 1, the output speed reduction mechanism 100 is wound around a first pulley 101 fixed to the input shaft 2, a second pulley 102 rotatably supported on the output shaft 3, and both pulleys 101 and 102. A belt-like body 103 made of a belt or chain that is hung, a second one-way clutch 104 provided on the output shaft 3, and a differential mechanism 105 are provided.

  The second one-way clutch 104 is provided between the second pulley 102 and the output shaft 3, and when the second pulley 102 attempts to rotate relative to the output shaft 3 on one side, the second pulley 102 idles. The second pulley 102 is configured to be fixed to the output shaft 3 when attempting to rotate relative to the other side.

  The second pulley 102 includes a fixed pulley 102a that is prevented from moving in the rotation axis direction, and a slide pulley 102b that is movable in the rotation axis direction with respect to the fixed pulley 102a. The slide pulley 102b is urged toward the fixed pulley 102a by an urging member 102c made of a coil spring.

  Due to the urging force of the urging member 102 c, a force is exerted on the second pulley 102 in a direction in which the width is narrowed, and a force in a direction in which the winding diameter of the belt state 103 in the second pulley 102 is increased is increased. Working.

  The first pulley 101 includes a fixed pulley 101a that is prevented from moving in the rotation axis direction, and a slide pulley 101b that is movable in the rotation axis direction with respect to the fixed pulley 101a. The differential mechanism 105 is disposed adjacent to the slide pulley 101b.

  The differential mechanism 105 includes a single pinion type planetary gear mechanism that includes a sun gear 201, a ring gear 203, and a carrier 207 that pivotally supports a planetary gear 205 that meshes with the sun gear 201 and the ring gear 203. The sun gear is connected to the pinion 70, and the carrier 207 is connected to the input shaft 2. On the outer periphery of the ring gear 203, three rolling elements 209 (see FIG. 10) made of rollers rotatably supported on the rolling element shaft 209a are provided at equal intervals in the circumferential direction.

  As shown in a cross section in FIG. 11A, a cam surface 101c that contacts the rolling element 209 is formed on the surface of the slide pulley 101b of the first pulley 101 on the differential mechanism 105 side. FIG. 11B shows the cam surface 101c in an unfolded state. When the eccentric amount R1 (rotation radius) is maximum by the cam surface 101c, the slide pulley 101b slides in the direction of the rotation axis toward the fixed pulley 101a by the rolling element 209 and the cam surface 101c, and the first pulley 101 is wound. The diameter is increased. At this time, the winding diameter of the second pulley 102 decreases against the biasing force of the biasing member 102 c in proportion to the increase in the winding diameter of the first pulley 101.

  The slide pulley 101b is provided with a maximum stopper 101d that engages with the rolling element 209 (contact portion) when the eccentric amount R1 (rotation radius) is maximum. When the adjustment drive source 14 is rotated by the maximum-side stopper 101d, the ring gear 203 rotates reversely as shown in FIG.

  When the ring gear 203 rotates in the reverse direction, both pulleys 101 and 102 also rotate in the reverse direction, and the second one-way clutch 104 rotates in the reverse direction unlike the forward movement, so that they mesh with each other. Therefore, when the rolling element 209 is engaged with the maximum-side stopper 101d using the driving force of the adjusting drive source 14, the output speed reduction mechanism 100 can perform reverse travel.

  Further, the cam surface 101c is provided with a flat portion 101e formed as a flat surface so as not to further increase the width of the first pulley 101 when the eccentric amount R1 (rotation radius) becomes a predetermined value or less. It has been. The output speed reduction mechanism 100 cannot make the winding radius of the belt-like body 103 zero. For this reason, when the eccentric amount R1 becomes equal to or less than a predetermined value, the winding radius on the first pulley 101 side is made constant by the flat portion 101e.

  The slide pulley 101b is provided with a minimum stopper 101f that engages with the rolling element 209 (contact portion) when the eccentric amount R1 (rotation radius) is minimum. As a result, the continuously variable transmission 1 is set to an infinite ratio (gear neutral state), and the rolling element 209 and the minimum stopper 101f are engaged with each other using the driving force of the adjusting drive source 14, and thus the internal combustion engine is used. The traveling drive source ENG can be started.

  FIG. 12 is a graph showing changes in the eccentric amount R1 (rotation radius) of the rotating disk 6 with the rotation angle of the pinion 70 as the horizontal axis. The cam surface 101c is also formed in an inclined surface like this curve. In addition, the horizontal line of FIG. 12 shows the position of the flat part 101e.

  The output speed reduction mechanism 100 of the present embodiment continuously changes the gear ratio (the rotational speed of the input shaft 2 / the rotational speed of the output shaft 3) of the output speed reduction mechanism 100 using the driving force of the adjustment drive source 14. Can do.

  FIG. 13 shows the rotation speeds of the elements of the first to third planetary gear mechanisms PGS1 to PGS3 and the differential mechanism 105 when the gear ratio of the output speed reduction mechanism 100 is reduced (changed to the high speed side). It is a thing. In FIGS. 13 to 17, the rotational speed on the vertical axis is a provisional speed when the traveling drive source ENG is rotating at a predetermined rotational speed in order to make the change in scale easy to understand. The rotational speed of each element of the present invention is not limited to this value. The rotational speed of the vertical axis in FIGS. 13 to 17 changes appropriately according to the rotational speed of the traveling drive source ENG, the gear ratios i, j, k of the planetary gear mechanisms PGS1 to PGS3, and the like.

  In addition, the horizontal axes of FIGS. 13 to 17 indicate the gear ratios i, j, and p of the planetary gear mechanisms PGS1 to PGS3 so that the rotational speeds of the elements of the planetary gear mechanisms PGS1 to PGS3 can be represented by straight lines. These are arranged at intervals corresponding to k (number of teeth of ring gear / number of teeth of sun gear).

  Further, in FIGS. 13 to 17, “A” is the rotation speed of the adjustment pinion 14a of the adjustment drive source 14, “C” is the rotation speed of the second intermediate gear G1b (see FIG. 6), and “D” is the first rotation speed. The rotational speed of the sun gear Sa of the single planetary gear mechanism PGS1, "Ca1" is the rotational speed of the first coupling body Ca-Cb, "F" is the rotational speed of the ring gear Ra, "G" is the rotational speed of the sun gear Sb, and "I" Is the rotational speed of the ring gear Rb, “J” is the rotational speed of the sun gear Sc, “Ca2” is the rotational speed of the carrier Cc, “M” is the rotational speed of the ring gear Rc, and “α” is the rotational speed of the sun gear 201 of the differential mechanism 105. “Ca3” indicates the rotational speed of the carrier 207, and “β” indicates the rotational speed of the ring gear 203.

  FIG. 14 is an enlarged view of the differential mechanism 105 shown in FIG.

  FIG. 15 shows the rotational speeds of the elements of the first to third planetary gear mechanisms PGS1 to PGS3 and the differential mechanism 105 when the speed ratio of the output speed reduction mechanism 100 is increased (changed to the low speed side). It is a thing.

  FIG. 16 shows an enlarged portion of the differential mechanism 105 of FIG.

  FIG. 17 shows the rotational speeds of the elements of the first to third planetary gear mechanisms PGS1 to PGS3 and the differential mechanism 105 when the speed ratio of the output speed reduction mechanism 100 is kept constant.

  In the continuously variable transmission 1 of the present embodiment, when the output deceleration mechanism 100 is operated to apply the engine brake, or the traveling drive source ENG is rotated using the rotational force of the driving wheel, the fuel cut is performed. When the second one-way clutch 104 is operated, the second pulley 102 is fixed to the output shaft 3 and the engine deceleration is applied by the output speed reduction mechanism 100 or the fuel consumption is improved. Can be planned.

  In this embodiment, the input end 2a and the cam disk 5 constitute the input shaft 2, and the input shaft 2 includes an insertion hole 60 formed by connecting the through holes 5a of the cam disk 5. Explained. However, the input shaft of the present invention is not limited to this. For example, the input shaft is formed in a hollow shaft shape having an insertion hole so that one end is opened, and a through hole is formed so that the input shaft can be inserted into a disc-shaped cam disk. May be formed larger than that of the first embodiment, and the cam disk may be splined to the outer peripheral surface of the input shaft configured in a hollow shaft shape.

  In this case, the input shaft formed of a hollow shaft is provided with a notch hole corresponding to the notch hole of the cam disk. The pinion inserted into the input shaft meshes with the internal teeth of the rotating disk via the notch hole of the input shaft and the notch hole of the cam disk.

  In the continuously variable transmission 1 of the present embodiment, the first to third planetary gear mechanisms PGS1 to PGS3 have been described as being configured by a single pinion type planetary gear mechanism. However, the first to third planetary gear mechanisms of the present invention are not limited to this. For example, although the transmission efficiency is inferior to that of a single pinion type, the planetary gear mechanism of the present invention includes a pair of planetary gears that mesh with a sun gear and a ring gear, one meshing with the sun gear and the other meshing with the ring gear. It can also be constituted by a double pinion type planetary gear mechanism composed of a carrier that is rotatably supported and revolved.

  In this case, one of the sun gear and the carrier of the first planetary gear mechanism is the first single element, the ring gear of the first planetary gear mechanism is the second single element, and the first planetary gear in the alignment order of the first planetary gear mechanism. The other of the sun gear and the carrier of the gear mechanism is the third single element. When the sun gear of the first planetary gear mechanism is the first single element and the carrier is the third single element, the distance between the sun gear and the ring gear of the first planetary gear mechanism and the distance between the ring gear and the carrier. The gear ratio of the first planetary gear mechanism may be set so that the ratio of the first planetary gear mechanism is equal to i: 1 described in the present embodiment. The same applies to the second planetary gear mechanism and the third planetary gear mechanism.

  In both the first and second embodiments, the input end 2 a and the cam disk 5 constitute an input shaft 2 (camshaft) as the input portion, and the input shaft 2 is a through hole of the cam disk 5. The thing provided with the insertion hole 60 comprised by 5a connecting was demonstrated. However, the input unit of the present invention is not limited to this, and for example, the input unit is configured by a hollow shaft-shaped input shaft having an insertion hole so that one end is opened, and a plurality of disk-shaped cam disks. A through hole may be formed larger than the through hole of the first embodiment so that the input shaft can be inserted into the disk, and the cam disk may be splined to the outer peripheral surface of the input shaft.

  In this case, the input shaft formed of a hollow shaft is provided with a notch hole corresponding to the notch hole of the cam disk. The pinion inserted into the input shaft meshes with the internal teeth of the rotating disk via the notch hole of the input shaft and the notch hole of the cam disk.

  In both the first and second embodiments, the one-way clutch 17 is used as the one-way rotation prevention mechanism. However, the one-way rotation prevention mechanism of the present invention is not limited to this, and the swing link 18 is not limited thereto. Alternatively, the swing link 18 capable of transmitting torque to the output shaft 3 may be configured by a two-way clutch (two-way clutch) configured to be able to switch the rotation direction with respect to the output shaft 3.

  In the present embodiment, the sun gear Sb (fourth single element) is provided with the brake B1 as the fixing mechanism. However, the configuration of the continuously variable transmission of the present invention is not limited to this. For example, the sun gear Sb (fourth single element) may be directly connected to the case 80 and fixed without using a brake as a fixing mechanism.

  In the present embodiment, the input unit is described as the input shaft 2 and the transmission unit is the pinion 70. However, the input unit and the transmission unit of the present invention are not limited thereto. For example, the input unit may be configured by the pinion 70 and the pinion shaft 72, and the transmission unit may be configured by the input shaft 2.

DESCRIPTION OF SYMBOLS 1 Continuously variable transmission 2 Input shaft 3 Output shaft 4 Turning radius adjustment mechanism 5 Cam disk (cam part)
5a Through-hole 5b Notch hole 5c Integrated cam part 6 Rotating disk (rotating part)
6a Receiving hole (inner circumference)
6b Internal gear 8 Reduction mechanism (Planetary gear mechanism)
14 Driving source for adjustment (electric motor)
15 connecting rod 15a input side annular portion 15b output side annular portion 16 connecting rod bearing 17 first one-way clutch 18 swing link 18a swing end portion 18b projecting piece 18c insertion hole 19 connecting pin 20 lever crank mechanism (four-bar link mechanism)
60 Insertion hole 70 Pinion 72 Pinion shaft 74 Bearing 80 Case 100 Output reduction mechanism 101 First pulley 101a Fixed pulley 101b Slide pulley 101c Cam surface 101d Maximum side stopper (maximum side locking portion)
101e Flat part 101f Minimum side stopper (minimum side locking part)
102 Second pulley 102a Fixed pulley 102b Slide pulley 102c Energizing member 103 Strip 104 104 Second one-way clutch 105 Differential mechanism 201 Sun gear 203 Ring gear 205 Planetary gear 207 Carrier 209 Rolling body (contact portion)
P1 Rotation center axis P2 Cam disc center point P3 Rotation disc center point La Distance between P1 and P2 Lb Distance between P2 and P3 R1 Eccentricity (distance between P1 and P3)
ENG Driving power source

Claims (4)

An input shaft to which the driving force of the driving source for traveling is transmitted;
An output shaft provided parallel to the input shaft;
A motion converting mechanism that has a rotating portion that rotates together with the input shaft and a swinging portion provided on the output shaft, and that converts the rotational motion of the rotating portion into the swinging motion of the swinging portion;
The swinging portion is fixed to the output shaft when the swinging portion is about to rotate relative to the output shaft, and the swinging portion is relatively positioned relative to the output shaft. A one-way rotation prevention mechanism that idles the rocking portion with respect to the output shaft when attempting to rotate;
A rotation radius adjusting mechanism having a pinion to which the driving force of the adjustment drive source is transmitted, and capable of adjusting the rotation radius of the rotating portion by adjusting a relative phase between the pinion and the input shaft;
An output speed reduction mechanism capable of decelerating the rotational speed of the output shaft using the driving force of the input shaft;
A continuously variable transmission that changes a gear ratio by changing a rotation radius of a rotating part,
The output deceleration mechanism is
A first pulley provided on the input shaft;
A second pulley provided on the output shaft;
A belt-like body wound around the first pulley and the second pulley and capable of transmitting power between the first pulley and the second pulley;
A differential mechanism comprising first to third three rotating elements;
Connecting the pinion to the first rotating element;
Connecting the input shaft to the second rotating element;
The third rotating element is provided with a contact portion that contacts a cam surface provided on a side surface of the first pulley,
The continuously variable transmission according to claim 1, wherein a width of the first pulley is changed by the cam surface by a change in a relative phase between the pinion and the input shaft. The continuously variable transmission according to claim 1,
The first pulley is provided with a maximum locking portion that locks the contact portion with the first pulley when the rotation radius of the rotating portion is maximum.
The differential mechanism is configured such that a rotation direction in which the contact portion is locked to the maximum-side locking portion is a reverse rotation direction that is a rotation direction when the vehicle travels backward. Continuously variable transmission. The continuously variable transmission according to claim 1 or 2,
The first pulley is provided with a minimum-side locking portion that locks the contact portion with the first pulley when the rotation radius of the rotating portion is minimum,
The differential mechanism is configured so that a rotation direction in which the contact portion is locked to the minimum-side locking portion is a forward rotation direction that is a rotation direction when the vehicle travels forward. Continuously variable transmission. The continuously variable transmission according to any one of claims 1 to 3,
A flat portion is provided on a portion of the cam surface on the side where the rotation radius of the rotating portion is minimized,
The continuously variable transmission according to claim 1, wherein, when the turning radius is equal to or less than a predetermined value, the flat portion makes the width of the first pulley constant without increasing.

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