JP5382882B2 - Continuously variable transmission mechanism and automobile drive system - Google Patents

Description

  The present invention is composed of four links (links) and four rotary pairs, and a four-bar linkage mechanism that converts rotational motion into rocking operation, with one node as the driving node and the opposite node as the driven node. The present invention relates to a continuously variable transmission mechanism and an automobile drive system.

  As a conventional continuously variable transmission mechanism of this type, there is known a system that converts the rotational motion of the output shaft of the engine into a swinging motion, and further converts the swinging motion into a rotational motion for output (for example, Patent Document 1). As shown in FIG. 20, the mechanism for converting the rotational motion described in Patent Document 1 into a swing motion includes a pinion 209 driven by an actuator, an eccentric disk 205 having internal teeth meshing with the teeth of the pinion 209, and The pinion 209 and the inner disk 204 for maintaining the mutual positional relationship of the eccentric disk 205 are provided.

  The center of rotation of the pinion 209 is located on the center of the output shaft of the engine (not shown), that is, the center axis of the input shaft of the continuously variable transmission mechanism (hereinafter referred to as the input center axis) O1, and the revolution center of the pinion 209 is continuously variable. It is located at the center Ox of the inner disk 204 that rotates integrally with the input shaft of the speed change mechanism (in reality, the position of the pinion 209 is fixed and does not revolve, so that the center Ox of the inner disk 204 is relative to the pinion 209. Have a relationship to revolve). In this case, the radius of the inner disk 204 is equal to the diameter of the pinion 209, and the revolution radius of the pinion 209 is equal to the radius of the pinion 209. The distance between the center O3 of the eccentric disk 205 and the center Ox of the inner disk 204 is equal to the radius of the pinion 209. As the inner disk 204 rotates, the center O3 of the eccentric disk 205 rotates about the input center axis O1, so that the eccentric disk 205 rotates eccentrically around the input center axis O1, thereby the eccentric disk. A connecting rod (connecting member) 206 rotatably connected to 205 is configured to swing.

  Thus, the eccentric amount when the eccentric disk 205 rotates eccentrically is the distance between the point O1 and the point O3, the distance between the point Ox and the point O3 is constant (the radius of the pinion 209), and the distance between the point Ox and the point O1. Is constant (the radius of the pinion 209), the distance between the point O1 and the point O3, that is, the position of the center Ox of the inner disk 204 relative to the line connecting the point O1 and the point O3, that is, The amount of eccentricity is determined.

  Therefore, when the amount of eccentricity is changed, the pinion 209 is rotated relative to the eccentric disk 205 by an actuator, and the inner disk 204 is rotated relative to the eccentric disk 205 as the tooth meshes. Then, the positional relationship between the points O1, O3, and Ox changes, and the distance between the points O1 and O3, that is, the amount of eccentricity changes. Therefore, the amount of eccentricity between the pinion 209 and the eccentric disk 205 can be changed by the rotation of the pinion 209, and the gear ratio can be changed accordingly. Even when maintaining a constant amount of eccentricity without changing the amount of eccentricity, a load torque is applied to the pinion 209 by the force acting on the connecting rod 206 to rotate the pinion 209. Therefore, depending on the magnitude of the force (pinion If the frictional force that can hold the pinion 209 is exceeded, a holding torque for holding the pinion 209 in a fixed position must be applied by the actuator.

German patent invention No. 102009039993

  By the way, the rotation of the pinion 209 is performed by using an actuator (not shown) as described above. However, in order to further improve energy efficiency and reduce the size of the actuator, it is necessary to reduce the torque applied to the pinion. It has become.

  The present invention has been made in view of the above-described circumstances, and its purpose is to reduce the power consumption of an actuator for maintaining the amount of eccentricity or changing the amount of eccentricity, and to improve energy efficiency. An object of the present invention is to provide a continuously variable transmission mechanism and an automobile drive system that can be realized.

In order to achieve the above-described object, the invention according to claim 1 is directed to an input center axis (for example, an input in an embodiment described later) by receiving rotational power from a prime mover (for example, ENG1, ENG2 in an embodiment described later). An input shaft rotating around the central axis O1) (for example, an input shaft 101 in an embodiment described later);
A first fulcrum (for example, described later) that is provided at equal intervals in the circumferential direction around the input center axis and that can change the amount of eccentricity relative to the input center axis (for example, the amount of eccentricity r1 in an embodiment described later) synchronously. A plurality of eccentric disks (for example, eccentric disks 104 in the embodiments described later) having the first fulcrum O3) in the embodiments at the respective centers and rotating together with the input shaft around the input center axis while maintaining the eccentric amount. )When,
An output member (for example, an output member 121 in an embodiment to be described later) that rotates around an output center axis (for example, an output center axis O2 in an embodiment to be described later) separated from the input center axis, and power in the rotational direction from the outside And an engaging member (for example, an input member 122 in the embodiment described later) and an engaging member (which locks or unlocks the input member and the output member). For example, when the rotational speed in the positive direction of the input member exceeds the rotational speed in the positive direction of the output member, the rotational power input to the input member is A one-way clutch that transmits to the output member, thereby converting the swinging motion of the input member into the rotational motion of the output member (e.g., implementation described below) The one-way clutch 120) in the state,
A second fulcrum provided with one end rotatably connected to the outer periphery of each eccentric disk around the first fulcrum, and the other end provided at a position separated from the output center axis on the input member of the one-way clutch. (For example, the second fulcrum O4 in the embodiment described later) is rotatably connected to the input member so that the rotational movement given from the input shaft to the eccentric disk is applied to the input member of the one-way clutch. A plurality of connecting members (e.g., connecting members 130 in the embodiments described later) to be transmitted as a swinging motion of
With
The input center axis, the first fulcrum, the second fulcrum, and the output center axis are rotation pairs, and a line segment connecting the input center axis and the output center axis is a first link (for example, a first link in an embodiment described later). Link Ln1), a line segment connecting the input center axis and the first fulcrum is a second link (for example, a second link Ln2 in an embodiment described later), and a line segment connecting the first fulcrum and the second fulcrum is a third link. (For example, the third link Ln3 in the embodiment described later), a line segment connecting the output center axis and the second fulcrum is a fourth link (for example, the fourth link Ln4 in the embodiment described later), and the first link is It is configured as a combination of a fixed joint, a plurality of four-bar linkage mechanisms with the second link as the driving node and the third link as the driven node.
The eccentric disk is formed as a disc centered on the first fulcrum, and a first circular hole (for example, a center Ox in an embodiment described later) is eccentric with respect to the center by a certain eccentric distance ( For example, an outer circumferential disk (for example, an outer circumferential disk 105 in an embodiment described later) having a first circular hole 106 in an embodiment described later and one end of the connecting member rotatably fitted on the outer periphery. The first circular hole of the outer peripheral disk is formed as a disk provided so as to be rotatable integrally with the input shaft and having a center deviated from the input central axis by the same distance as the constant eccentric distance. It is composed of an inner circumferential disk (for example, an inner circumferential disk 108 in an embodiment described later) that is rotatably fitted to the inner circumference,
A second circular hole (for example, a second circular hole 109 in an embodiment described later) is formed in the inner peripheral disk, with the input center axis being the center and a portion in the circumferential direction being open to the outer periphery of the inner peripheral disk. ) And a pinion that can rotate coaxially with the input center axis (for example, a pinion 110 in an embodiment described later) is accommodated in the second circular hole, and the teeth of the pinion correspond to the second circular hole. Meshing with an internal gear (for example, an internal gear 107 in an embodiment described later) formed on the inner periphery of the first circular hole of the outer peripheral disk through the outer peripheral opening,
Further, the pinion is rotated relative to the inner disk by rotating the pinion inside the second circular hole so that the teeth of the pinion and the teeth of the internal gear mesh with each other. Thereby, an actuator for adjusting the amount of eccentricity of the first fulcrum with respect to the input center axis corresponding to the length of the second link (for example, an actuator 180 in an embodiment described later) is connected.
The combination of the actuator, pinion, inner peripheral disk, and outer peripheral disk adjusts the amount of eccentricity of the first fulcrum with respect to the input center axis, and the vibration transmitted from the eccentric disk to the input member of the one-way clutch. The swinging angle of the dynamic motion (for example, swinging angle θ2 in an embodiment described later) is changed so that the rotational power input to the input shaft can be applied to the one-way clutch via the eccentric disk and the connecting member. A gear ratio variable mechanism (for example, a gear ratio in an embodiment described later) that can change the gear ratio at the time of transmission to the output member as rotational power and set the gear ratio to infinity by setting the eccentricity to zero. A continuously variable transmission mechanism (for example, a continuously variable / continuously variable transmission mechanism BD, BD1, BD2 in an embodiment described later) in which the variable mechanism 112) is configured;
In the rotational direction of the input shaft according to the rotational direction of the prime mover, the center of the inner peripheral disc, which is the center of revolution of the pinion, is located behind the line connecting the input central axis and the first fulcrum. As described above, control means (for example, control means 5 in an embodiment described later) for changing the amount of eccentricity of the first fulcrum with respect to the input center axis is provided.

The invention according to claim 2 is the structure of claim 1,
The prime mover is capable of rotating in the forward and reverse directions, and the center of the inner circumferential disc that is the center of revolution of the pinion is in the rotational direction of the input shaft according to the rotational direction of the prime mover. The amount of eccentricity of the first fulcrum with respect to the input center axis is changed so as to be located behind the line connecting the input center axis and the first fulcrum.

The invention according to claim 3 is the configuration according to claim 1 or 2,
In the case where the center of the inner peripheral disk, which is the center of revolution of the pinion, is positioned in front of the line connecting the input center axis and the first fulcrum in the rotation direction of the input shaft, the control means When the amount of eccentricity is maximum or zero, the center of the inner circumferential disc is positioned behind the line connecting the input center axis and the first fulcrum in the rotation direction of the input shaft. The amount of eccentricity of the first fulcrum with respect to the input center axis is changed.

The invention according to claim 4 is an automobile drive system (for example, an automobile drive system 1 in an embodiment described later),
Prime movers (for example, ENG1 and ENG2 in the embodiments described later);
The continuously variable transmission mechanism according to any one of claims 1 to 3,
A rotated drive member (for example, a driven member in an embodiment to be described later) that is connected to an output member of the one-way clutch and transmits the rotational power transmitted to the output member to a drive wheel (for example, a drive wheel 2 in an embodiment to be described later). A rotary drive member 11);
It is characterized by providing.

  According to the first and fourth aspects of the present invention, the direction of the torque applied to the pinion is optimized with respect to the rotational direction of the prime mover, and the pinion necessary for maintaining the speed ratio when power is transmitted through the connecting member. Torque can be reduced, and the power consumption of the actuator can be reduced.

  According to the second aspect of the present invention, even when the rotational direction of the prime mover changes, the power consumption of the actuator can be reduced.

  According to the invention of claim 3, the direction of torque applied to the pinion with respect to the rotation direction of the prime mover is optimized at an appropriate timing, and the power consumption of the actuator can be reduced.

1 is a skeleton diagram of an automobile drive system including a shift control device for a continuously variable transmission mechanism according to an embodiment of the present invention. FIG. It is sectional drawing which shows the specific structure of the infinite and continuously variable transmission mechanism which is the principal part of the system. It is the sectional side view which looked at the one part structure of the transmission mechanism from the axial direction. It is explanatory drawing of the first half part of the speed change principle by the gear ratio variable mechanism in the same speed change mechanism. FIG. 5B is a diagram showing a state in which the gear ratio i is set to “small” with “large”, and FIG. 5B is a diagram showing a state in which the eccentricity r1 is set to “medium” and the gear ratio i is set to “medium”. ) Is a diagram showing a state in which the eccentricity r1 is set to “small” and the transmission ratio i is set to “large”, and (d) is a state in which the eccentricity r1 is set to “zero” and the transmission ratio i is set to “infinity (∞)”. It is a figure which shows the state set to. FIG. 7 is an explanatory diagram of the latter half of the speed change principle of the speed change mechanism in the same speed change mechanism, wherein the input member 122 of the one-way clutch 120 swings when the speed change ratio i is changed by changing the eccentric amount r1 of the eccentric disk. FIG. 6A is a diagram showing a change in the angle θ2, and (a) shows a state in which the swing angle θ2 of the input member 122 becomes “large” by setting the eccentricity r1 to “large” and the transmission ratio i to “small”. FIG. 5B is a diagram showing a state in which the swing angle θ2 of the input member 122 is “medium” by setting the eccentricity r1 to “medium” and the gear ratio i to “medium”; ) Is a diagram showing a state where the swing angle θ2 of the input member 122 is “small” by setting the eccentricity r1 to “small” and the transmission ratio i to “large”. In the same speed change mechanism, when the eccentricity r1 (speed ratio i) of the eccentric disk rotating at the same speed as the input shaft is changed to “large”, “medium”, and “small”, the rotation angle θ of the input shaft and the one-way -It is a figure which shows the relationship of angular velocity (omega) 2 of the input member of a clutch. FIG. 6 is a diagram for explaining the principle of output extraction when power is transmitted from an input side (input shaft or eccentric disk) to an output side (output member of a one-way clutch) by a plurality of connecting members in the transmission mechanism. . It is explanatory drawing of the driving force transmission principle of the said infinite and continuously variable transmission mechanism comprised as a four-bar link mechanism. It is the model figure which added the link mechanism by the 5th, 6th link for adjusting the length (equivalent to eccentricity) of the 2nd link in the 4 node link mechanism. FIG. 6 is a diagram showing an example of adjusting the length of the second link (corresponding to the amount of eccentricity) in the four-bar linkage mechanism, wherein (a) maximizes the length of the second link (corresponding to the amount of eccentricity). When adjusted, (b) rotates the fifth and sixth links in a certain direction from the position (a), thereby reducing the length of the second link (corresponding to the amount of eccentricity) between a maximum and a minimum. When the value is adjusted to (c), the length of the second link (corresponding to the amount of eccentricity) is adjusted to the minimum, that is, zero, and (d) is constant from the position (c) to the fifth and sixth links. It is a figure which respectively shows the case where the length (equivalent to eccentricity) of the 2nd link is adjusted to the predetermined value between the maximum and minimum by rotating in a direction. It is a figure which shows the relationship of each element of the said infinite and continuously variable transmission mechanism when it corresponds to Fig.10 (a). It is a figure which shows the relationship of each element of the said infinite and continuously variable transmission mechanism when it corresponds to FIG.10 (b). It is a figure which shows the relationship of each element of the said infinite and continuously variable transmission mechanism when it corresponds to FIG.10 (c). It is a figure which shows the relationship of each element of the said infinite and continuously variable transmission mechanism when it corresponds to FIG.10 (d). When adjusting the length of the second link (corresponding to the amount of eccentricity) to a predetermined value between the maximum and minimum, there are two possible arrangements of the fifth and sixth links. FIG. 2B is a diagram when the state is A, i.e., (b) is a diagram when the state is B, a second state. It is explanatory drawing for the calculation of the torque which acts on the connection point Ox of the said 5th, 6th link in the said A state and the state of B, (a) is in the state of A, (b) is It is explanatory drawing in the state of B. (A) is a characteristic diagram showing the difference in torque (pinion torque) acting on the point Ox between the state A and the state B when the engine rotates CCW (counterclockwise), and (b) is a characteristic diagram showing the difference between the engine CW FIG. 6 is a characteristic diagram showing a difference in torque (pinion torque) acting on the point Ox between the state A and the state B when rotating (clockwise). It is a flowchart which shows the flow of control in the case where an engine carries out normal rotation (CCW rotation) and reverse rotation (CW rotation). (A) is a characteristic diagram when the engine is rotating in the forward direction (CCW rotation), (b) is a characteristic diagram when the engine is rotating in the reverse direction (CW rotation), and each of the upper diagrams shows the input member (outer outer) of the one-way clutch The figure showing the time change of the relationship between the speed of the ring) and the output member (inner ring) and the force F generated at the input point (first fulcrum O3) to the connecting member when the one-way clutch transmits torque. Is a diagram showing a time change of a sin value in a calculation formula of torque (pinion torque) acting on the point Ox in the state of A and in the state of B, and the lower diagram is in the state of the A It is a figure which shows the time change of the torque (pinion torque) which acts on the said point Ox in the state of A and B. FIG. It is sectional drawing which shows the mechanism which converts the rotational motion in the conventional continuously variable transmission mechanism into a rocking motion.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a skeleton diagram of an automobile drive system including a speed change control device for a continuously variable transmission mechanism according to the present embodiment, and FIG. 2 is a cross-sectional view showing a specific configuration of an infinite and continuously variable transmission mechanism that is a main part of the drive system. FIG. 3 and FIG. 3 are side sectional views of a part of the infinite and continuously variable transmission mechanism as viewed from the axial direction.

"overall structure"
This vehicle drive system 1 is provided on the downstream side of first and second engines (prime movers) ENG1 and ENG2 that independently generate rotational power, and first and second engines ENG1 and ENG2. First and second transmissions (transmission mechanisms) TM1 and TM2, first and second one-way clutches OWC1 and OWC2 provided at output portions of the transmissions TM1 and TM2, and these one-way clutches OWC1, Rotated drive member 11 that receives the output rotation transmitted through OWC 2, main motor generator (electric motor) MG 1 connected to this driven drive member 11, and output shaft S 1 of first engine ENG 1. Sub motor generator (engine starting means) MG2 and main and / or sub motor generator And Nereta MG1, the battery capable of power exchange between the MG2 (power storage unit) 8, a control unit 5 for controlling such travel pattern by controlling the various elements, and a.

  As shown in FIG. 3, each one-way clutch OWC <b> 1, OWC <b> 2 is arranged between an input member (clutch outer) 122, an output member (clutch inner) 121, and between these input member 122 and output member 121. A plurality of rollers (engagement members) 123 for bringing 122 and 121 into a locked state or an unlocked state, and a biasing member 126 for biasing the roller 123 in a direction to give the locked state. When the rotational speed of the input member 122 that receives the rotational power from the first transmission TM1 and the second transmission TM2 in the positive direction (arrow RD1 direction) exceeds the rotational speed of the output member 121 in the positive direction, When the input member 122 and the output member 121 are locked with each other, the rotational power input to the input member 122 is transmitted to the output member 121.

  The first and second one-way clutches OWC1 and OWC2 are arranged on the right and left sides of the differential device 10, and the output members 121 of the first and second one-way clutches OWC1 and OWC2 are different from each other. The first and second clutch mechanisms CL1 and CL2 are connected to the rotation driven member 11 together. The first and second clutch mechanisms CL1 and CL2 control the transmission / cutoff of power between the output members 121 of the first and second one-way clutches OWC1 and OWC2 and the driven member 11 to be rotated. Is provided. As these clutch mechanisms CL1 and CL2, other types of clutches (friction clutches and the like) can be used, but dog clutches are used because of low transmission loss.

  The driven member 11 is constituted by a differential case of the differential device 10, and the rotational power transmitted to the output member 121 of each one-way clutch OWC1, OWC2 is transmitted through the differential device 10 and the left and right axle shafts 13L, 13R. And transmitted to the left and right drive wheels 2. A differential case (rotary drive member 11) of the differential device 10 is provided with a differential pinion and a side gear (not shown). Dynamic rotation.

  The first and second engines ENG1 and ENG2 use different engines with high efficiency operation points. The first engine ENG1 is an engine with a small displacement, and the second engine ENG2 The engine has a larger displacement than the first engine ENG1. For example, the displacement of the first engine ENG1 is 500 cc, the displacement of the second engine ENG2 is 1000 cc, and the total displacement is 1500 cc. Of course, the combination of the displacements is arbitrary.

  The main motor generator MG1 and the driven member 11 are connected so that power can be transmitted when the drive gear 15 attached to the output shaft of the main motor generator MG1 and the driven gear 12 provided on the driven member 11 are engaged. Yes. For example, when the main motor generator MG1 functions as a motor, a driving force is transmitted from the main motor generator MG1 to the driven member 11 to be rotated. When the main motor generator MG1 functions as a generator, power is input from the driven member 11 to the main motor generator MG1, and mechanical energy is converted into electrical energy. At the same time, a regenerative braking force acts on the driven member 11 from the main motor generator MG1.

  The sub motor generator MG2 is directly connected to the output shaft S1 of the first engine ENG1, and performs mutual transmission of power with the output shaft S1. Also in this case, when the sub motor generator MG2 functions as a motor, the driving force is transmitted from the sub motor generator MG2 to the output shaft S1 of the first engine ENG1. When sub motor generator MG2 functions as a generator, power is transmitted from output shaft S1 of first engine ENG1 to sub motor generator MG2.

  In the drive system 1 having the above elements, the rotational power generated by the first engine ENG1 and the second engine ENG2 is transmitted through the first transmission TM1 and the second transmission TM2 to the first one-way The rotational power is input to the driven member 11 via the first one-way clutch OWC1 and the second one-way clutch OWC2 and input to the clutch OWC1 and the second one-way clutch OWC2.

  Further, in this drive system 1, the output shaft S2 and the rotated drive member 11 different from the power transmission via the second transmission TM2 between the output shaft S2 of the second engine ENG2 and the rotated drive member 11 are used. A synchro mechanism (clutch means also referred to as a starter clutch) 20 capable of connecting / disconnecting power transmission between them is provided. The synchro mechanism 20 always meshes with the driven gear 12 provided on the driven member 11 and rotates between the first gear 21 provided around the output shaft S2 of the second engine ENG2 and the second engine ENG2. A second gear 22 provided so as to rotate integrally with the output shaft S2 around the output shaft S2, and a sleeve for coupling or releasing the first gear 21 and the second gear 22 by being slid in the axial direction. 24. That is, the synchro mechanism 20 forms a power transmission path different from the power transmission path via the second transmission TM2 and the clutch mechanism CL2, and connects and disconnects the power transmission through this power transmission path.

<Configuration of transmission>
Next, the first and second transmissions TM1 and TM2 used in the drive system 1 will be described.
The first and second transmissions TM1 and TM2 are constituted by continuously variable transmission mechanisms having substantially the same configuration. The continuously variable transmission mechanism in this case is a kind of what is called an IVT (Infinity Variable Transmission = transmission mechanism in which the transmission ratio can be made infinite without using a clutch and the output rotation can be made zero). = I) can be changed steplessly, and the maximum value of the gear ratio can be set to infinity (∞), which is configured by an infinite and continuously variable transmission mechanism BD (BD1, BD2).

  2 and 3, the infinite and continuously variable transmission mechanism BD includes an input shaft 101 that rotates around an input center axis O1 by receiving rotational power from the engines ENG1 and ENG2, and an input shaft. 101 includes a plurality of eccentric discs 104 that rotate integrally with 101, the same number of connecting members 130 as the eccentric discs 104 for connecting the input side and the output side, and a one-way clutch 120 provided on the output side.

  The plurality of eccentric disks 104 are each formed in a circular shape centered on the first fulcrum O3. The first fulcrum O3 is provided at equal intervals in the circumferential direction of the input shaft 101. Each of the first fulcrums O3 can change the amount of eccentricity r1 with respect to the input center axis O1, and the input center axis O1 while maintaining the amount of eccentricity r1. Is set to rotate together with the input shaft 101. Accordingly, the plurality of eccentric disks 104 are provided to rotate eccentrically around the input center axis O1 as the input shaft 101 rotates while maintaining the eccentricity r1.

  As shown in FIG. 3, the eccentric disk 104 includes an outer peripheral disc 105 and an inner peripheral disc 108 that is provided on the input shaft 101 so as to be integrally rotatable. The inner circumferential disc 108 is formed as a thick disc having the center Ox biased by a certain eccentric distance with respect to the input center axis O1, which is the center axis of the input shaft 101. The outer peripheral side disk 105 is formed as a thick disk centered on the first fulcrum O3, and the center (first center fulcrum O3 of the inner peripheral side disk 108 and the center Ox) A first circular hole 106 having a matching point). And the outer periphery of the inner peripheral disk 108 is fitted to the inner periphery of the first circular hole 106 so as to be rotatable.

  Further, the inner circumferential disc 108 is provided with a second circular hole 109 centered on the input center axis O1 and having a part in the circumferential direction opened to the outer circumference of the inner circumferential disc 108. A pinion 110 is rotatably accommodated inside the two circular holes 109. The teeth of the pinion 110 are meshed with the internal gear 107 formed on the inner periphery of the first circular hole 106 of the outer peripheral side disk 105 through the opening on the outer periphery of the second circular hole 109. The ratio of the number of teeth of the tooth gear 107 is 1: 2.

  The pinion 110 is provided so as to rotate coaxially with the input center axis O1, which is the center axis of the input shaft 101. That is, the rotation center of the pinion 110 and the input center axis O1 that is the center axis of the input shaft 101 coincide with each other. As shown in FIG. 2, the pinion 110 is connected to an actuator 180 constituted by a DC motor and a speed reduction mechanism. The actuator 180 rotates the pinion 110 inside the second circular hole 109. Normally, by rotating the pinion 110 in synchronization with the rotation of the input shaft 101, and by giving the pinion 110 a rotational speed that is above or below the rotational speed of the input shaft 101 on the basis of the synchronous rotational speed. The pinion 110 is rotated relative to the input shaft 101.

  For example, when the pinion 110 and the output shaft of the actuator 180 are arranged so as to be connected to each other and the rotation of the actuator 180 causes a rotation difference with respect to the rotation of the input shaft 101, a reduction ratio is applied to the rotation difference. The pinion 110 is rotated by using a speed reduction mechanism (for example, a planetary gear) in which the relative angle between the input shaft 101 and the pinion 110 changes by the amount. At this time, if there is no rotational difference between the actuator 180 and the input shaft 101 and they are synchronized, the eccentricity r1 does not change.

  Therefore, when the pinion 110 is turned, the internal gear 107 that engages with the teeth of the pinion 110, that is, the outer peripheral disk 105 rotates relative to the inner peripheral disk 108, and thereby the rotation center of the pinion 110 is rotated. The positional relationship between the (input center axis O1), the center of the outer peripheral disk 105 (first fulcrum O3), and the revolution center Ox of the pinion 110 changes, and the center of the pinion 110 (input center axis O1) and the outer peripheral disk. The distance from the center of 105 (the first fulcrum O3) (that is, the eccentric amount r1 of the eccentric disk 104) changes.

  In this case, the rotation of the pinion 110 is set so that the center of the outer peripheral disc 105 (first fulcrum O3) can be matched with the center of the pinion 110 (input center axis O1), and both the centers match. By doing so, the eccentricity r1 of the eccentric disk 104 can be set to “zero”.

  The one-way clutch 120 also has an output member (clutch inner) 121 that rotates around an output center axis O2 that is distant from the input center axis O1, and an output center axis O2 that receives power from the outside in the rotational direction. A swinging ring-shaped input member (clutch outer) 122 and a plurality of members inserted between the input member 122 and the output member 121 to lock the input member 122 and the output member 121 with each other. It has a roller (engagement member) 123 and a biasing member 126 that biases the roller 123 in a direction to give a locked state, and is in the positive direction of the input member 122 (for example, the direction indicated by the arrow RD1 in FIG. 3) When the rotational speed exceeds the positive rotational speed of the output member 121, the rotational power input to the input member 122 is transmitted to the output member 121, and Accordingly, and it is capable of converting the oscillating motion of the input member 122 to the rotational motion of the output member 121.

  As shown in FIG. 2, the output member 121 of the one-way clutch 120 is configured as a member that is integrally continuous in the axial direction. However, the input member 122 is divided into a plurality of portions in the axial direction, and is eccentric. As many as the number of disks 104 and connecting members 130 are arranged so as to be able to swing independently in the axial direction. The roller 123 is inserted between the input member 122 and the output member 121 for each input member 122.

  A protruding portion 124 is provided at one circumferential position on each of the ring-shaped input members 122, and a second fulcrum O4 spaced from the output center axis O2 is provided on the protruding portion 124. And the pin 125 is arrange | positioned on the 2nd fulcrum O4 of each input member 122, and the front-end | tip (other end part) 132 of the connection member 130 is rotatably connected with the input member 122 by this pin 125. FIG.

  The connecting member 130 has a ring part 131 on one end side, and the inner periphery of the circular opening 133 of the ring part 131 is rotatably fitted to the outer periphery of the eccentric disk 104 via a bearing 140. Accordingly, one end of the connecting member 130 is rotatably connected to the outer periphery of the eccentric disk 104 in this way, and the other end of the connecting member 130 is the second fulcrum O4 provided on the input member 122 of the one-way clutch 120. Are connected to each other so that a four-bar linkage mechanism is formed with the input center axis O1, the first fulcrum O3, the output center axis O2, and the second fulcrum O4 as rotational pairs. The rotational motion given to the disk 104 is transmitted to the input member 122 of the one-way clutch 120 as the swinging motion of the input member 122, and the swinging motion of the input member 122 is converted into the rotational motion of the output member 121. The

  In that case, the outer peripheral side disk provided with the pinion 110, the inner periphery side disk 108 provided with the 2nd circular hole 109 which accommodates the pinion 110, and the 1st circular hole 106 which accommodates the inner periphery side disk 108 rotatably. The eccentric amount r1 of the eccentric disk 104 can be changed by moving the pinion 110 of the speed ratio variable mechanism 112 configured by the actuator 105 and the actuator 180 with the actuator 180. Then, by changing the amount of eccentricity r1, the swing angle θ2 of the input member 122 of the one-way clutch 120 can be changed, whereby the ratio of the rotational speed of the output member 121 to the rotational speed of the input shaft 101 ( Gear ratio: Ratio i) can be changed. That is, by adjusting the eccentric amount r1 of the first fulcrum O3 with respect to the input center axis O1, the swing angle θ2 of the swing motion transmitted from the eccentric disk 104 to the input member 122 of the one-way clutch 120 is changed. The speed ratio when the rotational power input to the input shaft 101 is transmitted as rotational power to the output member 121 of the one-way clutch 120 via the eccentric disk 104 and the connecting member 130 can be changed.

  In this case, the output shafts S1 and S2 of the first and second engines ENG1 and ENG2 are integrally connected to the input shaft 101 of the infinite and continuously variable transmission mechanism BD (BD1, BD2). Further, the one-way clutch 120, which is a component of the infinite and continuously variable transmission mechanism BD (BD1, BD2), is provided between the first transmission TM1 and the second transmission TM2 and the driven member 11 to be rotated. The first one-way clutch OWC1 and the second one-way clutch OWC2 also serve as each.

4 and 5 are explanatory diagrams of the speed change principle by the speed ratio variable mechanism 112 in the infinite and continuously variable transmission mechanism BD (BD1, BD2).
The speed ratio variable mechanism 112 is configured by a combination of the actuator 180, the pinion 110, the inner peripheral side disk 108, and the outer peripheral side disk 105 described above with reference to FIG. 3, and as shown in FIGS. The pinion 110 is rotated by the actuator 180 of the gear ratio variable mechanism 112 and the outer peripheral disk 105 is rotated with respect to the inner peripheral disk 108, whereby the input center axis O1 of the eccentric disk 104 (the rotation center of the pinion 110). ) Can be adjusted. In the infinite and continuously variable transmission mechanism BD (BD1, BD2), the swing angle θ2 of the swing motion transmitted from the eccentric disk 104 to the input member 122 of the one-way clutch 120 is adjusted by adjusting the eccentric amount r1. , So that the rotational power input to the input shaft 101 is transmitted as rotational power to the output member 121 of the one-way clutch 120 via the eccentric disk 104 and the connecting member 130 (ratio: i). In addition, the gear ratio can be set to infinity ∞ by setting the eccentricity r1 to zero.

  For example, as shown in FIGS. 4A and 5A, when the eccentric amount r1 of the eccentric disk 104 is set to “large”, the swing angle θ2 of the input member 122 of the one-way clutch 120 is increased. Therefore, a small gear ratio i can be realized. Further, as shown in FIGS. 4B and 5B, when the eccentric amount r1 of the eccentric disk 104 is set to “medium”, the swing angle θ2 of the input member 122 of the one-way clutch 120 is set to “medium”. Therefore, a medium speed ratio i can be realized. Further, as shown in FIGS. 4C and 5C, when the eccentric amount r1 of the eccentric disk 104 is set to “small”, the swing angle θ2 of the input member 122 of the one-way clutch 120 is decreased. Therefore, a large gear ratio i can be realized. Further, as shown in FIG. 4D, when the eccentric amount r1 of the eccentric disk 104 is set to “zero”, the swing angle θ2 of the input member 122 of the one-way clutch 120 can be set to “zero”. Therefore, the gear ratio i can be set to “infinity (∞)”.

  FIG. 6 shows that the eccentricity r1 (transmission ratio i) of the eccentric disk 104 that rotates at the same speed as the input shaft 101 is changed to “large”, “medium”, and “small” in the same transmission mechanism BD (BD1, BD2). FIG. 8 is a diagram showing the relationship between the rotation angle (θ) of the input shaft 101 and the angular velocity ω2 of the input member 122 of the one-way clutch 120, and FIG. 8 shows the relationship between the plurality of connecting members 130 in the transmission mechanism BD (BD1, BD2). It is a figure for demonstrating the output taking-out principle when motive power is transmitted from the input side (the input shaft 101 or the eccentric disk 104) to the output side (the output member 121 of the one-way clutch 120).

  When the input shaft 101 that rotates the eccentric disk 104 makes one rotation, the input member 122 of the one-way clutch 120 swings one reciprocating motion. As shown in FIG. 6, regardless of the value of the eccentricity r1 of the eccentric disk 104, the swing cycle of the input member 122 of the one-way clutch 120 is always constant. The angular velocity ω2 of the input member 122 is determined by the rotational angular velocity ω1 of the eccentric disk 104 (input shaft 101) and the eccentric amount r1.

  One end (ring portion 131) of a plurality of connecting members 130 connecting the input shaft 101 and the one-way clutch 120 is rotatably connected to an eccentric disk 104 provided at equal intervals in the circumferential direction around the input center axis O1. Therefore, the swinging motion brought about by the rotational motion of each eccentric disk 104 to the input member 122 of the one-way clutch 120 occurs in order at a constant phase as shown in FIG.

  At that time, transmission of power (torque) from the input member 122 to the output member 121 of the one-way clutch 120 is such that the rotational speed of the input member 122 in the positive direction (the direction of the arrow RD1 in FIG. It is performed only under conditions that exceed the rotational speed. That is, in the one-way clutch 120, meshing (locking) through the roller 123 occurs only when the rotational speed of the input member 122 becomes higher than the rotational speed of the output member 121, and the input member 122 is engaged by the connecting member 130. Is transmitted to the output member 121 to generate a driving force.

  After the driving by one connecting member 130 is finished, the rotational speed of the input member 122 is lower than the rotating speed of the output member 121, and the lock by the roller 123 is released by the driving force of the other connecting member 130, and free Return to the normal state (idle state). This is sequentially performed by the number of the connecting members 130, whereby the swinging motion is converted into a unidirectional rotational motion. Therefore, only the power of the input member 122 at a timing exceeding the rotational speed of the output member 121 is transmitted to the output member 121 in order, and the rotational power leveled almost smoothly is applied to the output member 121.

  Further, in this infinite / continuously variable transmission mechanism BD (BD1, BD2) of the four-bar linkage mechanism, by changing the eccentricity r1 of the eccentric disk 104, the transmission ratio (ratio = one revolution of the crankshaft of the engine) It is possible to determine whether to rotate the driven member only. In this case, by setting the eccentricity r1 to zero, the speed ratio i can be set to infinity, and the swing angle θ2 transmitted to the input member 122 is set to zero despite the engine rotating. can do.

  Therefore, as shown in FIG. 8, the infinite and continuously variable transmission mechanism BD (BD1, BD2) can be modeled as a four-bar linkage mechanism. That is, the infinite / continuously variable transmission mechanism BD (BD1, BD2) has an input center axis O1, a first fulcrum O3, a second fulcrum O4, and an output center axis O2 as rotational pairs, respectively, and the input center axis O1 and A line connecting the output center axis O2 is the first link Ln1, a line connecting the input center axis O1 and the first fulcrum O3 is the second link Ln2, and a line connecting the first fulcrum O3 and the second fulcrum O4 is the third link. Ln3, a line segment connecting the output center axis O2 and the second fulcrum O4 is a fourth link Ln4, the first link Ln1 is a fixed node, the second link is a driving node Ln2, and the third link Ln3 is a driven node. The mechanism is incorporated as a principle mechanism, and an infinite and continuously variable transmission mechanism BD (BD1, BD2) is configured by arranging a plurality of the four-bar linkage mechanisms in the rotational direction of the input shaft 101 with a phase shift. Say that It is possible.

  FIG. 9 shows fifth and sixth links for adjusting the length (corresponding to the eccentricity r1) of the second link Ln2 in the four-bar linkage mechanism of the infinite and continuously variable transmission mechanism BD (BD1, BD2). It is the model figure which added the link mechanism by.

  Here, the fifth link Ln5 includes the input center axis O1 that is the center of rotation of the pinion 110, the inner peripheral side disk 108 that is the center of revolution of the pinion 110, and the center Ox of the first circular hole 106 that accommodates it. Corresponds to connecting line segments. The sixth link Ln6 corresponds to a line segment connecting the point Ox and the first fulcrum O3. Further, the point Ox corresponds to a rotating pair that rotatably connects the fifth link Ln5 and the sixth link Ln6.

  Since the second link Ln2, the fifth link Ln5, and the sixth link Ln6 form a triangle and the lengths of the fifth link Ln5 and the sixth link Ln6 are fixed, the fifth link Ln5 and the sixth link Ln6 move. As a result, the length of the second link Ln2 (corresponding to the amount of eccentricity r1 of the eccentric disk 104) changes as the positional relationship among the points Ox, O1, and O3 changes.

  FIG. 10 is a diagram showing the positional relationship of each link when the length (eccentricity r1) of the second link Ln2 is adjusted by moving the fifth link Ln5 and the sixth link Ln6. When (a) adjusts the length (eccentricity r1) of the second link Ln2 to the maximum, (b) rotates the fifth link Ln5 in a certain direction from the position (a), and the second link Ln2 When the length (the amount of eccentricity r1) is adjusted to a predetermined value between the maximum and minimum, (c) is the length of the second link Ln2 by further rotating the fifth link Ln5 from the state of (b). When the height (eccentric amount r1) is adjusted to the minimum, that is, zero, (d) further rotates the fifth link Ln5 from the position of (c) in a fixed direction, thereby increasing the length of the second link Ln2 (eccentric amount r1). It is a figure which respectively shows the case where is adjusted to the predetermined value between the maximum and the minimum. FIGS. 11 to 14 show elements (pinion 110, inner peripheral side disk 108) of the infinite and continuously variable transmission mechanism BD (BD1, BD2) corresponding to the states of FIGS. 10 (a) to 10 (d). FIG. 5 is a diagram showing the relationship between the outer peripheral side disks 105).

  As shown in FIGS. 10 to 14, by rotating the pinion 110 relative to the eccentric disk 104 in a fixed direction, for example, the length (the eccentric amount r1) of the second link Ln2 is between the maximum and the minimum (zero). Can be adjusted freely. Also, when the relative rotation is performed in the reverse direction, the length (eccentricity r1) of the second link Ln2 can be freely adjusted between the maximum and minimum (zero).

  By the way, the direction in which the pinion 110 is rotated can be freely selected. As shown in FIG. 15, when adjusting the length (eccentricity r1) of the second link Ln2 between the maximum and minimum, The arrangement of the six links Ln5, Ln6 and the point Ox is adjusted under the condition in the state A as shown in FIG. 15A and the condition in the state B in the state shown in FIG. 15B. There are two possible cases. Here, the state of A is that the center Ox of the inner circumferential disk 108 that is the center of revolution of the pinion 110 is more than the line connecting the input center axis O1 and the first fulcrum O3 (the position overlapping the second link Ln2). This is a state located on the inner side (side closer to the output center axis O2 and the second fulcrum O4). In addition, the state of B means that the center Ox of the inner peripheral disk, which is the center of revolution of the pinion, is outside of the line connecting the input center axis O1 and the first fulcrum O3 (position overlapping the second link Ln2) (output). This is a state located on the side far from the center axis O2 and the second fulcrum O4.

  For example, when the rotation of the input shaft 101 is in the CCW direction (the direction of the arrow R1), the state A is that the center Ox of the inner peripheral disk, which is the center of revolution of the pinion, connects the input center axis O1 and the first fulcrum O3. This is a state located behind the connecting line (position overlapping the second link Ln2). Further, the state of B is a position where the center Ox of the inner peripheral disk, which is the center of revolution of the pinion, is located in front of the line connecting the input center axis O1 and the first fulcrum O3 (position overlapping the second link Ln2). It is a state to do.

  On the other hand, when the rotation of the input shaft 101 is in the CW direction (opposite to the arrow R1), the state A is that the center Ox of the inner peripheral disc that is the center of revolution of the pinion is the input center axis O1 and the first fulcrum. This is a state of being positioned in front of a line connecting O3 (a position overlapping with the second link Ln2). Further, the state of B means that the center Ox of the inner peripheral disk, which is the center of revolution of the pinion, is behind the line connecting the input center axis O1 and the first fulcrum O3 (position overlapping the second link Ln2). It is in a position.

  Both of these conditions can be adjusted to the length (eccentric amount r1) of the second link Ln2, but there are differences in the torques TA and TB applied to the pinion 110 under the two conditions.

  FIG. 16 shows the state of A when the rotation direction of the input shaft 101 is CCW rotation as indicated by the arrow R1 (section in which power from the engine side is transmitted to the output member 121 of the one-way clutch 120). It is explanatory drawing for the calculation of the torque which acts on the connection point Ox of the said 5th, 6th link in a state and the state of B, (a) is in the state of A, (b) is in the state of B It is explanatory drawing of. When the rotation direction of the input shaft 101 is reverse CW rotation, the phase is reversed, so that the magnitudes of TA and TB are reversed.

  In FIG. 16, force F is a reaction force of the first fulcrum O3 on the input side that opposes the tension of the connecting member 130 (third link Ln3). The force Fm is a component obtained by decomposing the force F, and is a force that acts as a rotational force on the first fulcrum O3. When the input shaft 101 rotates CCW as indicated by the arrow R1, the coupling member 130 (third link Ln3) generates a tension for transmitting power to the one-way clutch 120, and is the center point of the eccentric disk 104. The force F acts as a reaction force on the first fulcrum O3. When the torque around the point Ox at this time (hereinafter referred to as pinion torque) is calculated, in the state A, the pinion torque TA is expressed by the following equation (1), and in the state B, the pinion torque TB is The following equation (2) is obtained.

  Here, r is the length of each of the fifth link Ln5 and the sixth link Ln6, and corresponds to the radius of the pinion 110. Θ1 is the angle formed by the first link Ln1 and the second link Ln2, θ2 is the angle formed by the third link Ln3 and the first link Ln1, θact is the angle formed by the fifth link Ln5 and the sixth link Ln6, and Θ is the first angle This is the angle formed by the 6 links Ln6 and the third links Ln3.

となり、Ｂの状態では、

となる。 Since the value of Θ is geometrically related,

And in state B,

It becomes.

およびＢの状態のときの

は、力Ｆによるピニオントルク成分であり、各リンクの位置により異なるため時々刻々と変化する。しかし、入力軸１０１の回転方向により、決まった大小関係にあることが計算により確かめられた。なお、式（１）及び式（２）で、括弧の値を２で割るは、ピニオン１１０の歯数と内歯歯車１０７の歯数の比が１：２とされていることによる。 The sin value of the above formulas (1) and (2), that is, in the state of A

And in the state of B

Is a pinion torque component due to the force F, and varies depending on the position of each link, and changes every moment. However, it has been confirmed by calculation that there is a fixed magnitude relationship depending on the rotation direction of the input shaft 101. In the formulas (1) and (2), the value of the parenthesis is divided by 2 because the ratio between the number of teeth of the pinion 110 and the number of teeth of the internal gear 107 is 1: 2.

  FIG. 17A shows the calculation result of the magnitude relationship between TA and TB during CCW rotation, and FIG. 17B shows the calculation result of the magnitude relationship between TA and TB during CW rotation. Although the pinion torques TA and TB change according to the ratio, the magnitude relationship does not reverse during rotation of the input shaft in the same direction. In CCW rotation, TA ≦ TB, and in CW rotation, TA ≧ TB.

  Therefore, in the present embodiment, when the control means 5 controls the actuator 180, the center Ox of the inner circumferential disc 108, which is the revolution center of the pinion 110, is determined in the rotation direction of the input shaft 101 according to the rotation direction of the prime mover. The amount of eccentricity r1 of the first fulcrum O3 with respect to the input center axis O1 is changed so as to be located behind the line connecting the input center axis O1 and the first fulcrum O3 (line corresponding to the second link Ln2). Then, in the rotational direction of the input shaft 101, the actuator 180 causes the pinion 110 to move to the pinion 110 under the condition that the center Ox of the inner circumferential disc 108 is located behind the line connecting the input center axis O1 and the first fulcrum O3. The eccentric amount r1 of the first fulcrum O3 with respect to the input center axis O1 is changed or maintained by applying a rotational torque in the same rotational direction as the rotational direction of the input shaft 101.

  FIG. 18 is a flowchart showing the flow of control when the engine that is the prime mover rotates forward (CCW rotation) and reverse (CW rotation). FIG. 19A shows the case where the engine rotates forward (CCW rotation). Characteristic diagram, (b) is a characteristic diagram when the engine rotates in reverse (CW rotation), and the upper diagram shows the speed of the input member (outer ring) and output member (inner ring) of the one-way clutch and the one-way clutch. The figure which shows the time change of the relationship of the force F which generate | occur | produces in the input point (1st fulcrum O3) to a connection member when torque transmits, The figure of a middle stage is the said in the state of said A and the state of B The figure which shows the time change of the sine value in the calculation formula of the torque (pinion torque) which acts on the point Ox, and the lower figure shows the torque ( Pi It is a graph showing a temporal change of Ontoruku).

  Referring to the flowchart of FIG. 18, when controlling the actuator 180, first, the rotation direction of the prime mover (input shaft 101) is detected in step S101, and the rotation direction of the prime mover is the CCW direction based on the determination in step S102. Advances to step S103 to check whether the break direction is the A direction (state A). In the case of the A direction, the process returns to the main routine (not shown). If it is determined in step S103 that the bending direction is not the A direction, it waits for the eccentricity r1 to be maximum or zero in step S104 (waits for no bending), and is the eccentricity r1 maximum? When zero is reached, the process proceeds to step S105, and the next time the predetermined amount of eccentricity r1 is given, the bending direction is selected in the A direction and the process returns to the main routine.

  If the rotational direction of the prime mover is the CW direction according to the determination in step S102, the process proceeds to step S106, and it is checked whether the bending direction is the B direction (B state). In the B direction, the process returns to the main routine (not shown). If it is determined in step S106 that the bending direction is not the B direction, the process waits for the eccentricity r1 to reach the maximum or zero in step S107 (waits for no bending), and whether the eccentricity r1 is the maximum. When zero is reached, the process proceeds to step S108, and the next time the predetermined amount of eccentricity r1 is given, the bending direction is selected in the B direction and the process returns to the main routine.

  By controlling in this way, when the rotation direction of the input shaft 101 is the CCW direction, the torque TA is applied to the pinion 110 by the actuator 180 in the state A. When the rotation direction of the input shaft 101 is the CW direction, in the state B, the torque TB is applied to the pinion 110 by the actuator 180. In this case, as can be seen from the characteristic diagram shown in FIG. 19, in the engagement section (OWC transmission section), the state of A is smaller in the state of A during CCW rotation and the pinion torque component (sin value) is smaller, and the torque is lower during CW rotation. In the state B, the pinion torque component (sin value) is smaller and the torque is lower. Therefore, even when the rotational direction of the prime mover changes, the torque of the pinion 110 necessary to maintain the gear ratio can be reduced, and the power consumption of the actuator 180 can be reduced.

  As described above, according to the infinite and continuously variable transmission mechanism BD of the present embodiment, the inner circumference side circle that is the center of revolution of the pinion 110 in the rotation direction of the input shaft 101 according to the rotation direction of the engines ENG1 and ENG2. Since the amount of eccentricity r1 of the first fulcrum O3 with respect to the input center axis O1 is changed so that the center Ox of the plate 108 is located behind the line connecting the input center axis O1 and the first fulcrum O3, the engines ENG1, ENG2 The direction of the torque applied to the pinion 110 with respect to the rotation direction of the pinion 110 is optimized, and when transmitting power through the connecting member 130, the torque of the pinion 110 necessary to maintain the gear ratio can be reduced, The power consumption of the actuator 180 can be reduced.

  Further, the prime mover is capable of rotating in the forward and reverse directions, and the control means 5 causes the center Ox of the inner peripheral side disk 108, which is the revolution center of the pinion 110, in the rotational direction of the input shaft 101 according to the rotational direction of the prime mover. Since the eccentric amount r1 of the first fulcrum O3 with respect to the input center axis O1 is changed so as to be located behind the line connecting the input center axis O1 and the first fulcrum O3, the rotation direction of the prime mover is changed. Even if it exists, the torque of the pinion 110 required in order to maintain a gear ratio can be reduced, and the reduction of the power consumption of the actuator 180 can be aimed at.

  Further, the control means 5 is such that the center Ox of the inner circumferential disc 108 that is the revolution center of the pinion 110 is located in front of the line connecting the input center axis O1 and the first fulcrum O3 in the rotation direction of the input shaft 101. In this case, when the amount of eccentricity r1 is maximum or zero, the center Ox of the inner circumferential disc 108 is located behind the line connecting the input center axis O1 and the first fulcrum O3 in the rotation direction of the input shaft 101. Since the eccentric amount r1 of the first fulcrum O3 with respect to the input center axis O1 is changed so as to be positioned, the direction of the torque applied to the pinion 110 with respect to the rotation direction of the prime mover is optimized at an appropriate timing, and the actuator 180 Power consumption can be reduced.

  In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. In addition, the material, shape, dimensions, number, arrangement location, and the like of each component in the above-described embodiment are arbitrary and are not limited as long as the present invention can be achieved.

  For example, in the above-described embodiment, the case where the rotation output of the engine is shifted using the continuously variable transmission mechanism BD has been described. However, the present invention can also be applied to the case where the output of other prime movers such as an electric motor is shifted. it can.

  In the above-described embodiment, the output shaft of the engine has been described as being capable of rotating in the forward and reverse directions. However, the present invention can of course exhibit the effects of the present invention even when the output shaft of the engine rotates only in the forward direction or only in the reverse direction. .

DESCRIPTION OF SYMBOLS 101 Input shaft 104 Eccentric disk 105 Outer peripheral side disk 106 1st circular hole 107 Internal gear 108 Inner peripheral side disk 102 2nd circular hole 110 Pinion 112 Transmission ratio variable mechanism 120 One-way clutch 121 Output member 122 Input member 123 Roller (engagement member)
130 Connecting member 131 One end (ring part)
132 Other end 180 Actuator ENG Engine (prime mover)
BD Infinite and continuously variable transmission mechanism O1 Input center axis O2 Output center axis O3 First fulcrum O4 Second fulcrum r1 Eccentricity

Claims (4)

An input shaft that rotates around the input center axis by receiving rotational power from the prime mover;
The input center is provided at equal intervals in the circumferential direction around the input center axis and has a first fulcrum that can change the amount of eccentricity with respect to the input center axis in synchronization with each other, while maintaining the amount of eccentricity. A plurality of eccentric disks that rotate with the input shaft about an axis;
An output member that rotates around an output center axis that is distant from the input center axis, an input member that swings around the output center axis by receiving power in the rotational direction from the outside, and the input member and the output member An engaging member that is locked or unlocked, and the rotational power input to the input member when the rotational speed in the positive direction of the input member exceeds the rotational speed in the positive direction of the output member. A one-way clutch that converts the swinging motion of the input member into the rotational motion of the output member;
A second fulcrum provided with one end rotatably connected to the outer periphery of each eccentric disk around the first fulcrum, and the other end provided at a position separated from the output center axis on the input member of the one-way clutch. A plurality of connecting members that transmit the rotational motion given to the eccentric disk from the input shaft to the input member of the one-way clutch as the swinging motion of the input member,
With
The input center axis, the first fulcrum, the second fulcrum, and the output center axis are rotation pairs, and a line connecting the input center axis and the output center axis is a first link, and the input center axis and the first fulcrum are A line segment connecting the first fulcrum and the second fulcrum is a third link, a line segment connecting the output center axis and the second fulcrum is a fourth link, and the first link is a fixed node. The second link is a combination of a plurality of four-link mechanisms having a driving node and a third link as a driven node.
The eccentric disk is formed as a disk centered on the first fulcrum and has a first circular hole whose center is offset by a certain eccentric distance with respect to the center, and one end of the connecting member rotates on the outer periphery. An outer peripheral disc that is freely fitted, and a disc that is provided so as to be able to rotate integrally with the input shaft and that is decentered by the same distance as the constant eccentric distance with respect to the input center axis. An inner circumferential disk that is rotatably fitted to the inner circumference of the first circular hole of the outer circumferential disk,
The inner circumferential disc is provided with a second circular hole centered on the input center axis and having a part in the circumferential direction opened to the outer periphery of the inner circumferential disc, and the second circular hole has the second circular hole inside. An internal gear in which a pinion that is rotatable coaxially with the input center axis is accommodated, and the teeth of the pinion are formed on the inner periphery of the first circular hole of the outer peripheral disk through the opening of the outer periphery of the second circular hole. Meshing with
Further, the pinion is rotated relative to the inner disk by rotating the pinion inside the second circular hole so that the teeth of the pinion and the teeth of the internal gear mesh with each other. Thereby, an actuator for adjusting the amount of eccentricity of the first fulcrum with respect to the input center axis corresponding to the length of the second link is connected,
The combination of the actuator, pinion, inner peripheral disk, and outer peripheral disk adjusts the amount of eccentricity of the first fulcrum with respect to the input center axis, and the vibration transmitted from the eccentric disk to the input member of the one-way clutch. The gear ratio when changing the swing angle of the dynamic motion, whereby the rotational power input to the input shaft is transmitted as rotational power to the output member of the one-way clutch via the eccentric disk and the connecting member And a continuously variable transmission mechanism configured with a transmission ratio variable mechanism that can set the transmission ratio to infinity by setting the eccentricity to zero,
In the rotational direction of the input shaft according to the rotational direction of the prime mover, the center of the inner peripheral disc, which is the center of revolution of the pinion, is located behind the line connecting the input central axis and the first fulcrum. As described above, a continuously variable transmission mechanism comprising a control means for changing an eccentric amount of the first fulcrum with respect to the input center axis.   The prime mover is capable of rotating in the forward and reverse directions, and the center of the inner circumferential disc that is the center of revolution of the pinion is in the rotational direction of the input shaft according to the rotational direction of the prime mover. 2. The continuously variable transmission according to claim 1, wherein an eccentric amount of the first fulcrum with respect to the input center axis is changed so as to be located behind a line connecting the input center axis and the first fulcrum. mechanism.   In the case where the center of the inner peripheral disk, which is the center of revolution of the pinion, is positioned in front of the line connecting the input center axis and the first fulcrum in the rotation direction of the input shaft, the control means When the amount of eccentricity is maximum or zero, the center of the inner circumferential disc is positioned behind the line connecting the input center axis and the first fulcrum in the rotation direction of the input shaft. 3. The continuously variable transmission mechanism according to claim 1, wherein an eccentric amount of the first fulcrum with respect to the input center axis is changed. The prime mover;
The continuously variable transmission mechanism according to any one of claims 1 to 3,
A rotated drive member connected to the output member of the one-way clutch and transmitting the rotational power transmitted to the output member to a drive wheel;
An automobile drive system comprising:

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