JP6178915B2 - Continuously variable transmission - Google Patents

Description

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

  2. Description of the Related Art Conventionally, an input shaft as an input portion to which a driving force from a traveling drive 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 lever crank mechanisms (motion conversion) A four-bar linkage mechanism type continuously variable transmission including a mechanism is known (for example, see Patent Document 1).

  The lever crank mechanism disclosed in Patent Document 1 includes a rotation radius adjustment mechanism provided on an input shaft, a swing link pivotally supported on an output shaft, and a rotation radius adjustment mechanism at one end thereof. The connecting rod has an input-side annular portion that is externally fitted and the other end portion is connected to the swing end portion of the swing link.

  The turning radius adjusting mechanism includes a disk-shaped rotating disk having a through hole formed eccentrically from the center, a ring gear provided on the inner peripheral surface of the through hole, a first fixed to the input shaft and meshed with the ring gear. 1 pinion, a carrier as a transmission part to which the driving force from the adjustment drive source is transmitted, and two second pinions that are pivotally supported by the carrier so as to rotate and revolve, and mesh with the ring gear, respectively. Is done. The first pinion and the two second pinions are arranged so that a triangle whose apex is the central axis thereof is an equilateral triangle.

  When the rotational speed of the input shaft rotated by the driving source for driving and the carrier rotated by the driving source for adjustment are the same, the eccentric amount of the center point of the rotating disk with respect to the input center axis of the input shaft is maintained and rotated. The rotation radius of the disk is also kept constant. When the rotational speed of the input shaft that is rotated by the driving source for driving and the carrier that is rotated by the driving source for adjustment are different, the eccentric amount of the center point of the rotating disk with respect to the input center axis of the input shaft changes, and the rotating disk rotates. The radius also changes.

  When the rotation radius of the rotating disk is changed by the rotation radius adjusting mechanism, the swing width of the swing end of the swing link is also changed, the gear ratio is switched, and the rotational speed of the output shaft relative to the input shaft is controlled. .

  In such a continuously variable transmission, the distance between the center point of the equilateral triangle whose apex is the center axis of the three pinions and the input center axis of the input shaft, and the center point of the equilateral triangle and the center point of the rotating disk By setting the distance to be equal to each other, the input center axis and the center point of the rotating disk can be overlapped to make the amount of eccentricity zero. When the amount of eccentricity is 0, even when the input shaft is rotating, the swing width of the swing end of the swing link is 0, and the output shaft is not rotated.

JP 2012-1048 A

  In a continuously variable transmission equipped with a turning radius adjustment mechanism, when the travel drive source is started or stopped, the turning radius of the rotating part is reduced by energizing the rotation radius adjustment mechanism or the time lag until the travel drive source is stopped. There is a risk of unintentional changes. If the turning radius of the rotating part changes unintentionally, it is necessary to check the turning radius of the rotating part again when restarting the traveling drive source, and to transmit power to the drive wheels. There is a risk of hindering a smooth start.

  The present invention has been made in view of the above points, and an object of the present invention is to provide a continuously variable transmission that prevents the rotation radius of the rotating portion from unintentionally changing when the traveling drive source is started or stopped. .

[1] In order to achieve the above object, the present invention provides:
An input unit that is rotated by a driving force transmitted from a driving source for traveling; and
An output shaft disposed parallel to the rotation center axis of the input unit;
A rotation unit that can rotate integrally with the input unit; a rocking unit that is pivotally supported by the output shaft; and a connecting body that connects the rotation unit and the rocking unit. A plurality of motion conversion mechanisms that convert motion into a swing motion of the swing portion;
The swinging portion is fixed to the output shaft when attempting to rotate relative to the output shaft on one side, and the swinging portion is idled relative to the output shaft when attempting to rotate relative to the other side. A one-way rotation prevention mechanism
A turning radius adjusting mechanism capable of adjusting the turning radius of the rotating part using the driving force of the adjusting drive source;
A continuously variable transmission comprising a turning radius control unit for controlling the adjustment drive source;
The rotation radius control unit can execute a maintenance process for controlling the adjustment drive source so as to maintain the rotation radius of the rotation unit.
The turning radius control unit is
When the travel drive source is started, before the travel drive source is started, energize the adjustment drive source to execute the maintenance process,
When the travel drive source is stopped, the maintenance process is terminated after the travel drive source is stopped ,
The turning radius adjusting mechanism includes:
A cam portion that rotates eccentrically with respect to the rotation center axis of the input portion;
A rotating part rotatable in an eccentric state with respect to the cam part;
A transmission unit that transmits the driving force of the adjustment drive source via a differential mechanism;
The differential mechanism includes a first input element to which power from the driving source for traveling is transmitted via the input unit, a second input element to which driving force of the adjustment driving source is transmitted, and the transmission A transmission element coupled to the section,
The differential mechanism is configured such that when the first input element and the transmission element rotate at the same speed in the same direction, the rotation speed of the second input element is “0”.
The differential mechanism is composed of first to third planetary gear mechanisms having three single elements of a sun gear, a carrier, and a ring gear,
The three single elements of the first planetary gear mechanism are designated as the first single element, the second single element, and the third single element from the one side in the alignment order in the collinear diagram, and the three single elements of the second planetary gear mechanism are collinear. The first single element, the fifth single element, and the sixth single element are arranged from one side in the arrangement order in the figure, and the three single element elements of the third planetary gear mechanism are arranged from one side in the arrangement order in the collinear diagram, the seventh single element, As 8 single element, 9 single element,
The second single element and the fifth single element are connected to form a first connecting body, the third single element and the ninth single element are connected to form a second connecting body, 6 single elements and the seventh single element are connected to form a third connected body,
The second connector is the first input element, the first single element is the second input element, and the eighth single element is the transmission element;
The fourth single element is fixed non-rotatably;
The gear ratio between the first planetary gear mechanism and the second planetary gear mechanism is determined by the distance between the first single element and the second single element in the collinear diagram, the second single element, and the third single element. So that the ratio between the fourth unit element and the fifth unit element and the ratio between the fifth unit element and the sixth unit element are equal. set and said Rukoto.

  According to the present invention, the turning radius control unit executes the maintenance process before the traveling drive source is started when the traveling drive source is started, and the traveling radius when the traveling drive source is stopped. The maintenance process ends after the drive source is stopped. Thus, the maintenance process is always executed when the driving source for traveling is started or stopped.

  Therefore, according to the continuously variable transmission of the present invention, due to the time lag when the traveling drive source is turned on / off, the rotation radius of the rotating part is unintentionally caused by the driving force of the traveling drive source after the maintenance process is completed. It is possible to prevent the change.

  [2] In the present invention, the travel drive source is an internal combustion engine, and includes a starter motor for starting the travel drive source, and the turning radius control unit requests a start request for starting the travel drive source. When the information can be received, the turning radius control unit, when receiving the start request information, energizes the adjustment drive source and executes the maintenance process before energizing the starter motor.

  [3] Also, in the present invention, the turning radius control unit includes stop request information for requesting stop of the travel drive source and stop completion information for confirming that the stop of the travel drive source is completed. When receiving the stop request information, the turning radius control unit executes the maintenance process until receiving the stop completion information, and ends the maintenance process after receiving the stop completion information.

  [4] In the present invention, the turning radius adjusting mechanism includes a cam portion that rotates in an eccentric state with respect to the rotation center axis of the input portion, and a rotating portion that is rotatable in an eccentric state with respect to the cam portion. A transmission unit that transmits the driving force of the adjusting drive source via a differential mechanism, and the differential mechanism includes a first input element that transmits power from the travel drive source via the input unit; The second input element to which the driving force of the adjusting drive source is transmitted and the transmission element connected to the transmission unit, and the differential mechanism includes the first input element and the transmission element at the same speed in the same direction. When rotating, the rotation speed of the second input element is configured to be “0”.

  [5] The differential mechanism of the present invention is composed of first to third three planetary gear mechanisms having three single elements of a sun gear, a carrier, and a ring gear, and the three single elements of the first planetary gear mechanism. Are the first single element, the second single element, and the third single element from one side in the alignment order in the collinear diagram, and the three single element elements of the second planetary gear mechanism from the one in the alignment order in the collinear diagram, The fifth single unit element, the sixth single unit element, and the three single unit elements of the third planetary gear mechanism from the one side in the alignment order in the alignment chart, the seventh single unit element, the eighth single unit element, the ninth single unit element, the second single unit The first unit is configured by connecting the element and the fifth unit element, the second unit is configured by connecting the third unit element and the ninth unit element, and the second unit is the first input element. The first single element is the second input element and the eighth single element A transmission element, the fourth single direction element can be configured to be non-rotatably fixed.

1 is a partial cross-sectional view showing a first embodiment of a continuously variable transmission according to the present invention. Explanatory drawing which shows the motion conversion mechanism of the continuously variable transmission of 1st Embodiment. It is explanatory drawing which shows the change state of the rotation radius of the rotation part of 1st Embodiment, FIG. 3A shows a state when a rotation radius is "maximum", and FIG. 3B shows when a rotation radius is "medium" FIG. 3C shows a state when the turning radius is “small”, and FIG. 3D shows a state when the turning radius is “0”. FIG. 4 is an explanatory diagram showing a change in the swing range of the swing portion with respect to a change in the rotation radius of the rotary portion, and FIG. 4A shows the swing range of the swing portion when the rotation radius is maximum. 4B shows the swinging range of the swinging part when the turning radius is “medium”, and FIG. 4C shows the swinging range of the swinging part when the turning radius is “small”. The flowchart which shows control when starting the drive source for driving | running | working of the rotation radius control part of 1st Embodiment. The flowchart which shows the control when stopping the drive source for driving | running | working of the rotation radius control part of 1st Embodiment. The skeleton figure which shows 2nd Embodiment of the continuously variable transmission of this invention. FIG. 10 is a collinear diagram illustrating a shift state of the differential mechanism of the second embodiment. The alignment chart which shows the state which maintains the gear ratio of the differential mechanism of 2nd Embodiment.

[First Embodiment]
An embodiment of a continuously variable transmission according to the present invention will be described with reference to the drawings. The continuously variable transmission according to the present embodiment is a transmission capable of setting the speed ratio h (h = rotational speed of the input shaft / rotational speed of the output shaft) to infinity (∞) and the rotational speed of the output shaft to “0”. It is a kind of so-called IVT (Infinity Variable Transmission).

  1 to 4, a four-bar linkage type continuously variable transmission 1 rotates around a rotation center axis P1 by receiving a rotational driving force from a driving source such as an internal combustion engine or an electric motor. An input shaft 2 serving as an input unit, an output shaft 3 that is arranged in parallel to the rotation center axis P1, and that transmits rotational power to a driving wheel of the vehicle via a differential gear, a propeller shaft, etc., not shown, and an input shaft 2 And six turning radius adjusting mechanisms 4 provided on the head.

  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 provided with a notch hole 5b that opens in a direction opposite to the direction decentered with respect to the rotation center axis P1 and communicates the outer peripheral surface of the cam disk 5 with the through hole 5a. Each set of cam disks 5 is arranged so as to make a round in the circumferential direction of the input shaft 2 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. As a result, the input shaft 2 (camshaft) is configured in a hollow shape with one end opened on the side opposite to the driving source for traveling. The cam disk 5 located at the other end on the traveling drive source side is formed integrally with the input shaft 2. That is, the cam disk 5 located at the end on the traveling drive source side is formed integrally with the input end 2a. As a method of integrally forming the cam disk 5 and the input shaft 2, 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. 2, the rotating disk 6 has a cam disk 5 center point P2 and a rotating disk 6 center point P3, a distance La between the rotation center axis P1 and the center point P2, and a center point P2 and a 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.

  The pinion 70 is rotatable relative to the input shaft 2 in the insertion hole 60 of the input shaft 2 (camshaft) so as to be concentric with the rotation center axis P1 and at a position corresponding to the inner teeth 6b of the rotary disk 6. 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 and the pinion shaft 72 may be connected 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 through the bearing 74. The differential 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 differential mechanism 8. That is, in the first embodiment, the pinion 70 is a transmission unit of the present invention.

  The differential mechanism 8 includes a planetary gear mechanism, and includes a sun gear 9, a first ring gear 10 connected to the camshaft 51, a second ring gear 11 connected to the pinion shaft 72, the sun gear 9, and the first gear. A carrier 13 is provided that supports a stepped pinion 12 composed of a large-diameter portion 12a meshing with the ring gear 10 and a small-diameter portion 12b meshing with the second ring gear 11 so as to be able to rotate and revolve.

  The sun gear 9 is connected to the rotating shaft of the adjusting drive source 14 composed of an electric motor for the pinion shaft 72. When the rotational speed of the adjusting drive source 14 is the same as the rotational speed of the input shaft 2, the sun gear 9 and the first ring gear 10 rotate at the same speed, and the sun gear 9, the first ring gear 10, the second ring gear 11, and the like. The four elements of the carrier 13 are in a locked state where relative rotation is impossible, and the pinion shaft 72 connected to the second ring gear 11 rotates at the same speed as the input shaft 2.

  When the rotational speed of the adjustment drive source 14 is made slower than the rotational speed of the input shaft 2, the rotational speed of the sun gear 9 is Ns, the rotational speed of the first ring gear 10 is NR1, and the gear ratio between the sun gear 9 and the first ring gear 10 (first The rotational speed of the carrier 13 is (j · NR1 + Ns) / (j + 1) where j is the number of teeth of one ring gear 10 / the number of teeth of the sun gear 9). The gear ratio between the sun gear 9 and the second ring gear 11 ((number of teeth of the second ring gear 11 / number of teeth of the sun gear 9) × (number of teeth of the large diameter portion 12a of the stepped pinion 12 / number of teeth of the small diameter portion 12b). ) Is k, the rotational speed of the second ring gear 11 is {j (k + 1) NR1 + (k−j) Ns} / {k (j + 1)}.

  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 a one-way clutch 17 serving as a one-way rotation blocking mechanism.

  The one-way clutch 17 as a one-way rotation prevention mechanism is provided between the swing link 18 and the output shaft 3, and swings on the output shaft 3 when attempting to rotate relative to the output shaft 3 on one side. The link 18 is fixed, and the swing link 18 is idled with respect to the output shaft 3 when attempting to rotate relative to the other side.

  The swing link 18 is formed in an annular shape, and a swing end portion 18a connected to the output-side annular portion 15b of the connecting rod 15 is provided above 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.

  FIG. 3 shows the positional relationship between the pinion shaft 72 and the rotating disk 6 in a state where the eccentricity R1 as the rotation radius of the rotation radius adjusting mechanism 4 is changed. FIG. 3A shows a state where the eccentric amount 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.

  FIG. 3B shows a state in which the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 3A, and FIG. 3C shows a state in which the eccentric amount R1 is set to “small” which is further smaller than that in FIG. The gear ratio h is “medium” which is larger than the gear ratio h in FIG. 3A in FIG. 3B and “large” which is larger than the gear ratio h in FIG. 3B in FIG. FIG. 3D 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 rotation radius adjustment mechanism 4 changes the eccentric amount R1 as the rotation radius, whereby the rotation radius of the rotating disk 6 as the rotating portion (the miracle drawn by P3 as the input side fulcrum) The radius of the circle is adjustable. In the present embodiment, the eccentric amount R1 and the rotation radius of the rotary disk 6 are defined to be the same.

  In the first embodiment, the turning radius adjustment 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. Therefore, the lever crank mechanism 20 corresponds to the motion conversion mechanism of the present invention.

  The continuously variable transmission 1 of the first 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 a swing link 18 provided on the output shaft 3 via a one-way clutch 17, the swing link 18 is pushed and pulled by the connecting rod 15 to swing. When the swing link 18 moves, 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, the output shaft 3, the force of the swing motion of the swing link 18 is not transmitted, and the swing 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 (not shown) that controls the adjustment drive source 14. The control unit is configured by an ECU that is an electronic unit configured by a CPU, a memory, and the like, and controls the adjustment drive source 14 by executing a control program held in a storage unit such as a memory by the CPU. It functions to adjust the eccentric amount R1 of the rotating disk 6.

  Moreover, the driving motor for transmitting power to the input shaft 2 of the present embodiment is provided with a starting motor used for starting the driving drive source. When the start of the travel drive source is requested, start request information is transmitted to the control unit and the turning radius control unit.

  The control unit includes a turning radius control unit. In the control unit, the driving force (torque) and rotation speed of the driving source for driving, the rotation speed of driving wheels and driven wheels, the current driving speed (vehicle speed) of the vehicle, the opening of the throttle valve, the current eccentricity R1, etc. From the predetermined information (predetermined vehicle information), a target eccentricity amount as a target rotation radius is obtained. Then, the output of the adjustment drive source 14 is adjusted so that the current eccentricity R1 as the current rotational radius becomes the target eccentricity.

  Next, with reference to FIG. 5, the control when the turning radius control unit is turned on (vehicle power on) will be described.

  First, in step 11, it is confirmed whether or not an ignition switch (vehicle power switch) is turned on. When the ignition switch is turned on, the process proceeds to step 12 to check whether or not the shift position is the parking range or the neutral range. When the shift position is the parking range or the neutral range, the process proceeds to step 13 where the driver of the adjustment drive source 14 is energized to start the adjustment drive source 14.

  Then, in step 14, it is confirmed whether or not the adjustment drive source 14 is in a start complete state. If the adjustment drive source 14 is not in the start complete state, the process returns to step 13. In the present embodiment, the processes in steps 13 and 14 correspond to the maintenance process of the present invention. If the adjustment drive source 14 is in the start complete state in step 14, the process proceeds to step 15 to set a permission flag for permitting the start of the travel drive source.

  Then, the process proceeds to step 16, and the control unit confirming that the permission flag is set starts to start the travel drive source. Then, the process proceeds to step 17 where it is confirmed whether or not the starting of the traveling drive source has been completed. If the starting of the traveling drive source has not been completed, the process returns to step 16. If the start of the driving source for traveling is completed in step 17, the current process is terminated.

  If the ignition switch is off in step 11, the process branches to step 18 where standby control is performed until the ignition switch is turned on, and the current process is terminated. If the shift position is not in the parking range or neutral range in step 12, the shift position is not correct, so an error is notified to the driver and the process proceeds to step 18 where standby control is executed and the current process is terminated. To do.

  Next, referring to FIG. 6, the control when the turning radius control unit is turned off (vehicle power off) will be described. First, in step 21, it is confirmed whether or not an ignition off signal (stop request information) has been received. If an ignition-off signal (stop request information) is received, the process proceeds to step 22 to execute a maintenance process for controlling the adjustment drive source 14 so that the rotation radius of the rotary disk 6 is not changed. Then, the process proceeds to step 23, and a stop permission flag is set to permit the stop of the travel drive source.

  And it progresses to step 24 and the process which stops a drive source for driving | running | working is performed. And it progresses to step 25 and it is confirmed whether the drive source for driving | running | working stopped. If the traveling drive source is not completely stopped, the process returns to step 24, and the execution of the process for stopping the traveling drive source is continued.

  If it is confirmed in step 25 that the travel drive source is stopped, in other words, if stop completion information is received, the process proceeds to step 26 where the adjustment drive source 14 is set so as to maintain the rotational radius of the rotary disk 6. The process to be controlled is terminated, and the current process is terminated.

  If it is determined in step 21 that an ignition off signal has not been received, the process branches to step 27 to execute a normal turning radius control process based on predetermined vehicle information, and the current process is terminated.

  According to the continuously variable transmission 1 of the first embodiment, when the travel drive source is started, the turning radius control unit maintains steps 13 and 14 in FIG. 5 before the travel drive source is started. When the process is executed and the travel drive source is stopped, the maintenance process (step 22) is terminated after the travel drive source is stopped (step 26). Thus, when the travel drive source is started or stopped, the maintenance process of step 13, step 14, and step 22 is always executed.

  Therefore, according to the continuously variable transmission 1 of the first embodiment, after the maintenance process is completed due to a time lag when the driving source for driving is turned on and off, the rotating disk 6 as a rotating part is driven by the driving force of the driving source for driving. Can be prevented from unintentionally changing.

[Second Embodiment]
A continuously variable transmission 1 according to a second embodiment of the present invention will be described with reference to FIGS. The continuously variable transmission 1 of the second embodiment has the same configuration except that the configuration of the differential mechanism 8 is different from that of the continuously variable transmission 1 of the first embodiment. Are denoted by the same reference numerals and description thereof is omitted.

  As shown in FIG. 7, the differential mechanism 8 of the second embodiment 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. 8 shows a collinear chart that can represent the rotation 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. 8 and 9, 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 camshaft 51 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 by a straight line is shown in the middle stage of FIG. The three single elements of the second planetary gear mechanism PGS2 are arranged in order of arrangement in the collinear diagram from one side, and in this embodiment, in order from the right side in FIG. 8, 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. 8 shows a collinear diagram that can represent the rotation speeds of the three single elements of the sun planetary gear Sc, the carrier Cc, and the ring gear Rc of the third planetary gear mechanism PGS3 by straight lines. The three single elements of the third planetary gear mechanism PGS3 are arranged in order of arrangement in the collinear diagram from one side, and in the present embodiment, in order from the right side in FIG. 8, 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 differential mechanism 8, the adjustment drive source 14, and the like, and releases the fixation. It is configured to be switchable to an open state. In the present embodiment, the brake B1 is always fixed.

  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. 2, the rotating disk 6 is eccentric with respect to the cam disk 5 so that the distance La and the distance Lb are the same, so that 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. 9 shows an alignment chart in a state where 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. 9, the rotational speed of the second coupling body Ra-Rc coupled to the input shaft 2 is the same as that of the third planetary gear mechanism coupled to the pinion 70. When the rotation speed of the carrier Cc (eighth single element) of PGS3 is “N1”, that is, when the gear 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 second embodiment, when the speed 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 is understood that the rotation speed of the sun gear Sa (first single element) as the second input element may be controlled to be “0”. The collinear diagram of FIG. 8 shows a state where the gear ratio h is changed.

  Also in the continuously variable transmission 1 according to the second embodiment, when the travel drive source is started, the turning radius control unit maintains the processing in steps 13 and 14 in FIG. 5 before the travel drive source is started. When the travel drive source is stopped, the maintenance process (step 22) is terminated after the travel drive source is stopped (step 26). Thus, when the travel drive source is started or stopped, the maintenance process of step 13, step 14, and step 22 is always executed.

  Therefore, according to the continuously variable transmission 1 of the second embodiment, after the maintenance process is completed due to a time lag when the driving source for driving is turned on and off, the rotating disk 6 as a rotating unit is driven by the driving force of the driving source for driving. Can be prevented from unintentionally changing.

  In the continuously variable transmission 1 of the second embodiment, the first to third planetary gear mechanisms PGS <b> 1 to PGS <b> 3 are configured by single pinion type planetary gear mechanisms. 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.

[Other Embodiments]
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 both the first and second embodiments, the sun gear Sb (fourth single element) is provided with the brake B1 as a 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 both the first and second embodiments, the input unit is described as the input shaft 2 and the transmission unit is the pinion 70, but the input unit and the transmission unit of the present invention are not limited to this. 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 2a Input end part 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 Differential mechanism (Planetary gear mechanism)
14 Driving source for adjustment (electric motor)
15 connecting rod 15a input side annular part 15b output side annular part 16 connecting rod bearing 17 one-way clutch (one-way rotation prevention mechanism)
18 Oscillating link (oscillating part)
18a Swing end 18b Projection piece 18c Insertion hole 19 Connection pin 20 Lever crank mechanism (four-bar linkage mechanism)
60 Insertion hole 70 Pinion (Transmission part)
72 Pinion shaft 74 Bearing 80 Case P1 Rotation center axis P2 Cam disk center point P3 Rotation disk center point La P1 and P2 distance Lb P2 and P3 distance R1 Eccentricity (distance between P1 and P3)

Claims (3)

An input unit that is rotated by a driving force transmitted from a driving source for traveling; and
An output shaft disposed parallel to the rotation center axis of the input unit;
A rotation unit that can rotate integrally with the input unit; a rocking unit that is pivotally supported by the output shaft; and a connecting body that connects the rotation unit and the rocking unit. A plurality of motion conversion mechanisms that convert motion into a swing motion of the swing portion;
The swinging portion is fixed to the output shaft when attempting to rotate relative to the output shaft on one side, and the swinging portion is idled relative to the output shaft when attempting to rotate relative to the other side. A one-way rotation prevention mechanism
A turning radius adjusting mechanism capable of adjusting the turning radius of the rotating part using the driving force of the adjusting drive source;
A continuously variable transmission comprising a turning radius control unit for controlling the adjustment drive source;
The rotation radius control unit can execute a maintenance process for controlling the adjustment drive source so as to maintain the rotation radius of the rotation unit.
The turning radius control unit is
When the travel drive source is started, before the travel drive source is started, energize the adjustment drive source to execute the maintenance process,
When the travel drive source is stopped, the maintenance process is terminated after the travel drive source is stopped,
The turning radius adjusting mechanism includes:
A cam portion that rotates eccentrically with respect to the rotation center axis of the input portion;
A rotating part rotatable in an eccentric state with respect to the cam part;
A transmission unit that transmits the driving force of the adjustment drive source via a differential mechanism;
The differential mechanism includes a first input element to which power from the driving source for traveling is transmitted via the input unit, a second input element to which driving force of the adjustment driving source is transmitted, and the transmission A transmission element coupled to the section,
The differential mechanism is configured such that when the first input element and the transmission element rotate at the same speed in the same direction, the rotation speed of the second input element is “0”.
The differential mechanism is composed of first to third planetary gear mechanisms having three single elements of a sun gear, a carrier, and a ring gear,
The three single elements of the first planetary gear mechanism are designated as the first single element, the second single element, and the third single element from the one side in the alignment order in the collinear diagram, and the three single elements of the second planetary gear mechanism are collinear. The first single element, the fifth single element, and the sixth single element are arranged from one side in the arrangement order in the figure, and the three single element elements of the third planetary gear mechanism are arranged from one side in the arrangement order in the collinear diagram, the seventh single element, As 8 single element, 9 single element,
The second single element and the fifth single element are connected to form a first connecting body, the third single element and the ninth single element are connected to form a second connecting body, 6 single elements and the seventh single element are connected to form a third connected body,
The second connector is the first input element, the first single element is the second input element, and the eighth single element is the transmission element;
The fourth single element is fixed non-rotatably;
The gear ratio between the first planetary gear mechanism and the second planetary gear mechanism is determined by the distance between the first single element and the second single element in the collinear diagram, the second single element, and the third single element. So that the ratio between the fourth unit element and the fifth unit element and the ratio between the fifth unit element and the sixth unit element are equal. A continuously variable transmission characterized by being set. The continuously variable transmission according to claim 1,
The driving source for traveling is an internal combustion engine;
A starting motor for starting the driving source for traveling;
The turning radius control unit can receive start request information requesting start of the driving source for traveling,
The turning radius control unit, when receiving the start request information, energizes the adjustment drive source and executes the maintenance process before energizing the starter motor. Machine. The continuously variable transmission according to claim 1,
The turning radius control unit is capable of receiving stop request information for requesting the stop of the travel drive source and stop completion information for confirming that the stop of the travel drive source has been completed,
The rotation radius control unit, when receiving the stop request information, executes the maintenance process until receiving the stop completion information, and ends the maintenance process after receiving the stop completion information. A continuously variable transmission.