JP2016044693A - Non-stage transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a non-stage transmission that is simple in compact size and has a superior operability.SOLUTION: This invention relates to a non-stage transmission 100 having a rotational speed ratio between a first shaft 1 and a second shaft 2 changed in non step manner comprising a first pulley 10 having a pair of mating sheaves 11, 12 rotatably attached to the first shaft 1 under nonelastic manner in which a space between sheave surfaces 11A, 12A of both sheaves 11, 12 can be adjusted; a second pulley 20 having a pair of mating sheaves 21, 22 rotatably attached to the second shaft 2 under nonelastic manner in which a space between sheave surfaces 21A, 22A of both sheaves 21, 22 can be adjusted; a first ring 30 held between the sheave surfaces 11A, 12A of both sheaves 11, 12 at the first pulley 10; a second ring 40 held between the sheave surfaces 21A, 22A of both sheaves 21, 22 at the second pulley 20; and a winding member 50 wound around the first ring 30 and the second ring 40.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a continuously variable transmission.

  Conventionally, as a belt-type continuously variable transmission that continuously changes the rotation speed ratio between the first shaft and the second shaft, a pair of opposed sheaves are attached to the first shaft so as to be able to rotate together, and the sheave surfaces of both sheaves A first pulley having an adjustable interval, and a second pulley having a pair of opposed sheaves attached to the second shaft so as to be able to rotate together, and an interval between the sheave surfaces of both sheaves being adjustable. And a flexible winding member wound around the first pulley and the second pulley. The winding member is sandwiched between the sheave surfaces of both sheaves in the first pulley, and is sandwiched between the sheave surfaces of both sheaves in the second pulley.

  In the belt-type continuously variable transmission, the effective diameter of the first pulley (pulley) is increased by moving the winding member in the radial direction of the first pulley by expanding or reducing the distance between the sheave surfaces of the sheaves constituting the first pulley. The radius of rotation of the contact portion of the sheave surface with the winding member can be changed. In addition, by expanding or reducing the distance between the sheave surfaces of both sheaves constituting the second pulley, the effective diameter of the second pulley can be changed by moving the winding member in the radial direction of the second pulley. When the effective diameter of the first pulley is enlarged (or reduced), the effective diameter of the second pulley is changed and adjusted so that the effective diameter of the second pulley is relatively reduced (or enlarged), thereby comparing with the rotation speed of the first shaft. Thus, the rotational speed of the second shaft can be increased (or decelerated) to achieve a desired gear ratio.

JP 2009-144751

The conventional belt type continuously variable transmission has the following problems.
(1) A flexible winding member is sandwiched between sheave surfaces in which the distance between both sheaves in each of the first pulley and the second pulley is expanded and contracted, and the winding member is moved in the radial direction of each pulley. There is a difficulty in the structure and production of the winding member.

  (2) In the continuously variable transmission, when transmitting power, the slipping between the sheave surface of the first pulley and the winding member is prevented, and the slipping between the sheave surface of the second pulley and the winding member is prevented. It is necessary to control increase / decrease of the tension applied to the member so as to match the increase / decrease of the transmission torque.

  However, in the belt type continuously variable transmission, the tension applied to the winding member is controlled by changing and adjusting the effective diameters of the first pulley and the second pulley. Therefore, the adjustment of the effective diameters of the first pulley and the second pulley is not only a relative change adjustment for realizing a desired gear ratio on the first shaft and the second shaft as described above, but also a winding member. It is also necessary to make relative changes and adjustments to apply tension to the winding member that does not cause slippage on the sheave surfaces of the first pulley and the second pulley. Complicated and difficult.

  Not only to achieve a desired transmission ratio between the first shaft and the second shaft, but also the tension applied to the winding member so that the winding member does not slip on the sheave surfaces of the first pulley and the second pulley. In order to apply, it is necessary to enlarge and reduce the distance between the sheave surfaces of the first pulley and the second pulley to relatively change and adjust the effective diameters of the sheave surfaces of the first pulley and the second pulley. The drive source (hydraulic pump, motor, etc.) for adjusting the distance between the first shaft and the second shaft is also increased in capacity (weight, space).

  (3) In the continuously variable transmission, the distance adjustment amount between the sheave surfaces of the first pulley and the second pulley to obtain the required shift width is reduced, thereby shortening the shift operation time and narrowing the shift operation space. Therefore, it is desirable to reduce the sheave angles of the first pulley and the second pulley.

  However, in the belt-type continuously variable transmission, when the sheave angles of the first pulley and the second pulley are made small, the belt bites into each pulley due to the wedge effect, and the loose side belt becomes entangled with each pulley and becomes difficult to come off.

  An object of the present invention is to provide a continuously variable transmission that is simple, compact, and excellent in operability.

  According to a first aspect of the present invention, in a continuously variable transmission that continuously changes the rotational speed ratio between the first shaft and the second shaft, a pair of opposed sheaves are attached to the first shaft so as to be able to rotate together. A first pulley having an adjustable interval between the sheave surfaces of the sheave and a pair of opposing sheaves are attached to the second shaft so as to be able to rotate together, and the interval between the sheave surfaces of both sheaves can be adjusted. A second ring, a first ring sandwiched between sheave surfaces of both sheaves in the first pulley, a second ring sandwiched between sheave surfaces of both sheaves in the second pulley, a first ring and a second ring It is made to have a winding member wound around.

  According to a second aspect of the present invention, in the first aspect of the invention, the pair of sheaves of the first pulley includes a fixed sheave and a movable sheave that moves in the axial direction with respect to the fixed sheave. A pair of sheaves of the second pulley are composed of a fixed sheave and a movable sheave that moves in the axial direction with respect to the fixed sheave, and both sheaves are tapered in the opposite directions. A sheave surface is provided.

  According to a third aspect of the present invention, in the first or second aspect of the present invention, the first ring and the second ring further include a ring having a gear surface on the outer periphery thereof, and the winding member is the first ring and the second ring. It is made of a toothed wrapping member that can be wound around two rings without slipping.

  (a) As shown in FIG. 3, the first ring and the second ring are pressed against and contacted with the first pulley and the second pulley by the initial tension T and the transmission force W acting on the winding member. Power is transmitted by a traction drive effect based on contact pressure acting on P or a friction drive effect. Thereby, the rotation input given to the first shaft is transmitted to the second shaft through the first pulley, the first ring, the winding member, the second ring, and the second pulley, and is taken out as the rotation output from the second shaft. Is done.

  (b) When power is not transmitted (including when idling), as shown in FIG. 3 (A), the winding member wound on the first ring sandwiched between the first pulleys has a tension side, The same initial tension T acts on the loose side, and the first ring is pressed at one contact point P against the sheave surfaces of both sheaves in the first pulley by both tensions T and T. At this time, the first ring has a moment Ma exerted around the contact point P by the tension T acting on the tension side winding member and a tension T acting on the loose side winding member around the contact point P. The moment Mb balances (Ma = Mb) and stabilizes in a specific posture (in this specific posture, the length of a straight line hanging from the contact point P to each of the tension-side winding member and the loose-side winding member is La. , Lb, Ma = T · La and Mb = T · Lb. From Ma = Mb, La = Lb).

  At this time, similarly, the second ring is also stabilized in a specific posture.

  (c) Next, when the rotational input F is applied to the first shaft and the power is transmitted, as shown in FIG. 3B, the winding member wound around the first ring sandwiched between the first pulleys In this case, the resultant tension of the initial tension T and the transmission force W acts on the tension side, and only the initial tension T acts on the loose side, and the first ring pulled by the transmission force W is in contact with the first pulley. P rolls around the first axis and moves in the direction opposite to the rotation input F. At this time, in the first ring, the moment Ma exerted around the contact point P by the resultant force T and the transmission force W acting on the tension-side winding member and the tension T acting on the loose-side winding member are described above. The moment Mb exerted around the contact point P is balanced (Ma = Mb), and the sheave surface of both sheaves in the first pulley is again pressed against the sheave surface of the first pulley at the one contact point P to be stabilized (in this specific posture, the contact When the lengths of the straight lines hanging from the point P to the tension member and the slack member are La and Lb, Ma = (T + W) La, Mb = T · Lb, and Ma = Mb (La = T · Lb / (T + W)).

  At this time, similarly, the second ring is again stabilized in the specific posture.

  (d) From the above-mentioned (a) and (b), the first ring and the second ring are always unambiguous by the tension T and the transmission force W both when the power is not transmitted and when the power is transmitted. Therefore, a guide roller or the like is not required to stably hold the posture of each ring by pressing against the sheave surfaces of both sheaves of the first pulley or the second pulley in a specific posture determined by

  (e) As described above (d), the first ring and the second ring are always uniquely determined by the tension T and the transmission force W, both when power is not transmitted and when power is transmitted. Since it is pressed against the sheave surface of both sheaves in the first pulley or the second pulley in the posture and stabilized, not only the forward rotation operation of the first shaft but also the reverse rotation operation of the first shaft or the rotation input from the second shaft Power can also be transmitted for driving to which (engine brake or the like) is applied.

  (f) A rigid first ring and second ring are sandwiched between sheave surfaces in which the distance between both sheaves in each of the first pulley and the second pulley is expanded and contracted, and these rings are connected in the radial direction of each pulley at the time of shifting. The structure and production of each ring is simplified.

  (g) As described above (c), when the rotational input F is applied to the first shaft and power is transmitted, the first ring causes the contact point P with the first pulley to roll around the first shaft. And move in the opposite direction to the rotation input F. In other words, the center O1 of the first ring rolls around the first axis and moves in the direction opposite to the rotation input F. At this time, the center O2 of the second ring rolls around the second axis and moves in the same direction as the rotational output G. This movement of the center O1 of the first ring and the center O2 of the second ring means that the distance (span) between the centers of both rings increases (the centers O1, O2 of both rings when power is not transmitted). Is on a straight line connecting the centers of the first axis and the second axis, and its span is So (FIG. 4A), whereas the centers O1 and O2 of both rings when power is transmitted. Moves in the above-mentioned direction around the first axis and the second axis, and the span is Sw (So <Sw) (FIG. 4B).

  That is, the span of the first ring and the second ring is increased, and as a result, the winding member wound around both the rings is elastically stretched to increase its tension. Accordingly, a tension corresponding to the increase in the transmission force W is generated in the winding member during power transmission, and this tension presses the first ring and the second ring against the sheave surface of the first pulley and the sheave surface of the second pulley. Automatically increases and prevents slipping of both rings.

  Therefore, when the transmission force increases, the distance between the sheave surfaces of the first pulley and the second pulley is such that the first ring and the second ring do not slide relative to the sheave surfaces of the first pulley and the second pulley. There is no need to intentionally adjust. A continuously variable transmission that is simple and excellent in operability by adjusting the distance between the sheave surfaces of the first pulley and the second pulley only in order to achieve a desired gear ratio between the first shaft and the second shaft. Can be built.

  (h) Since the first ring and the second ring are rigid bodies, the force that each ring bites into each pulley on the pull side becomes the force that causes the loose side to separate from each pulley, and each sheave angle of the first pulley and the second pulley Even if it is made small, there is no possibility that each ring will be entangled with each pulley and difficult to come off. Therefore, each sheave angle of the first pulley and the second pulley is reduced, and as a result, the distance adjustment amount between the sheave surfaces of the first pulley and the second pulley for obtaining a necessary shift width is reduced, and the shift operation time is reduced. Can be shortened and the space for shifting operation can be reduced.

FIG. 1 is a schematic diagram showing the overall configuration of a continuously variable transmission. FIG. 2 is a schematic plan view showing the basic structure of the continuously variable transmission. 3A and 3B show the principle of power transmission of the continuously variable transmission. FIG. 3A is a schematic front view showing a state where power is not transmitted, and FIG. 3B is a schematic front view showing a power transmission state. 4A and 4B show the span change of the first ring and the second ring due to the power transmission of the continuously variable transmission. FIG. 4A is a schematic front view showing the span when power is not transmitted. FIG. It is a model front view which shows the span of.

  The continuously variable transmission 100 shown in FIG. 1 and FIG. 2 is used not only for automobiles but also for vehicles other than automobiles.

  The continuously variable transmission 100 is provided between, for example, a first shaft 1 (input shaft) connected to the engine side and a second shaft 2 (output shaft) connected to the tire side. And the rotation speed ratio of the second shaft 2 are steplessly changed.

  The continuously variable transmission 100 includes a first pulley 10, a second pulley 20, a first ring 30, a second ring 40, and a flexible winding member 50.

  The continuously variable transmission 10 has a pair of opposing sheaves 11 and 12 attached to the first shaft 1 so as to be able to rotate along with the first shaft 1, and the distance between the sheave surfaces 11 A and 12 A of the sheaves 11 and 12 can be adjusted by the speed change operation means 60. Has been. In the present embodiment, one sheave 11 of the continuously variable transmission 10 is a fixed sheave 11 that is integrally fixed to the first shaft 1. The other sheave 12 of the continuously variable transmission 10 is spline-coupled to the outer periphery of the first shaft 1 to be a movable sheave 12 that moves in the axial direction with respect to the fixed sheave 11. The first shaft 1 is pivotally supported by bearings 1A and 1B at one end side and the other end side of a portion where the first pulley 10 (sheaves 11 and 12) is provided. Both sheaves 11 and 12 have tapered sheave surfaces 11A and 12A inclined in opposite directions, and a V-groove 13 having a sheave angle θ is formed between both sheave surfaces 11A and 12A.

  The second pulley 20 has a pair of opposed sheaves 21 and 22 attached to the second shaft 2 so as to be able to rotate along with the second shaft 2, and the speed change operation means 60 can adjust the distance between the sheave surfaces 21 A and 22 A of both sheaves 21 and 22. Has been. In the present embodiment, one sheave 21 of the second pulley 20 is a fixed sheave 21 that is integrally fixed to the second shaft 2. The other sheave 22 of the second pulley 20 is splined to the outer periphery of the second shaft 2, and serves as a movable sheave 22 that moves in the axial direction with respect to the fixed sheave 21. The second shaft 2 is pivotally supported by bearings 2A and 2B at one end side and the other end side of the portion where the second pulley 20 (the sheaves 21 and 22) is provided. Both sheaves 21 and 22 have tapered sheave surfaces 21A and 22A inclined in opposite directions, and a V-groove 23 having a sheave angle θ is formed between the sheave surfaces 21A and 22A.

  The first ring 30 is sandwiched between the sheave surfaces 11 </ b> A and 12 </ b> A of the sheaves 11 and 12 in the first pulley 10. As shown in FIG. 2, the first ring 30 is formed of an annular rigid ring, and both side surfaces are power transmission surfaces 31 and 32. The first ring 30 is partially fitted in the V-groove 13 formed by the sheave surfaces 11A and 12A of the sheaves 11 and 12, and the power transmission surfaces 31 and 32 are spaced from the sheave surfaces 11A and 12A. Engage with no contact.

  The second ring 40 is sandwiched between the sheave surfaces 21 </ b> A and 22 </ b> A of the sheaves 21 and 22 in the second pulley 20. As shown in FIG. 2, the second ring 40 is formed of an annular rigid ring, and both side surfaces are power transmission surfaces 41 and 42. The second ring 40 is partially fitted in the V-groove 23 formed by the sheave surfaces 21A and 22A of the sheaves 21 and 22, and the power transmission surfaces 41 and 42 are spaced from the sheave surfaces 21A and 22A. Engage with no contact.

  The winding member 50 includes a first ring 30 sandwiched between the sheave surfaces 11A and 12A of the sheaves 11 and 12 of the first pulley 10 and sheave surfaces 21A and 22A of the sheaves 21 and 22 of the second pulley 20. Is wound around the second ring 40 sandwiched between them with a certain initial tension applied thereto. In the present embodiment, the first ring 30 and the second ring 40 are sprocket rings having gear surfaces 33 and 43 on their outer circumferences, and the winding member 50 meshes with the gear surfaces 33 and 43 so as not to slip. It is assumed to consist of a wound sprocket chain. The first ring 30 and the second ring 40 are toothed rings having gear faces on the outer periphery thereof, and the winding member 50 is formed of a toothed belt that meshes with the gear faces and is wound without slipping. It may be assumed.

  Therefore, in the continuously variable transmission 100, the distance between the sheave surfaces 11 </ b> A, 12 </ b> A of the sheaves 11, 12 in the first pulley 10 and the groove width of the V-groove 13 are adjusted by the shift operation means 60. The effective diameter R1 of the first pulley 10 with which the power transmission surfaces 31 and 32 of the ring 30 are engaged in contact is changed, and the distance between the sheave surfaces 21A and 22A of the sheaves 21 and 22 in the second pulley 20 and thus V By adjusting the groove width of the groove 23, the effective diameter R2 of the second pulley 20 with which the power transmission surfaces 41, 42 of the second ring 40 are engaged in contact is changed, and the rotational speed N1 of the first shaft 1 and the second The rotational speed N2 of the shaft 2 is changed as N2 = (R1 / R2) · N1. At this time, the speed change operation means 60 increases the second effective diameter R1 of the first pulley 10 as much as possible so as not to loosen the winding member 50 even when the speed is changed. The effective diameter R2 of the pulley 20 is reduced (or enlarged).

  In this embodiment, the speed change operating means 60 is fitted on the other end side of the first shaft 1 so that the pressing collar 61 is relatively rotatable on the outer periphery of the portion sandwiched between the bearing 1B and the movable sheave 12 of the first pulley 10. A thrust bearing 62 is interposed between the outer end surface of the movable sheave 12 and the end surface of the pressing collar 61 opposite to the movable sheave 12, and a ball screw groove 61A screwed on the outer periphery of the pressing collar 61 is inserted with a ball (not shown). A ball screw groove (not shown) screwed on the inner periphery of the driven gear 63 is screwed, and the driven gear 63 is rotatably supported by the bearing 64 and is axially fixed. The speed change operation means 60 has a drive gear 65 provided at one end of a speed change operation shaft 60 </ b> S driven by an electric motor meshed with the driven gear 63 described above.

  The speed change operating means 60 is fitted on the outer periphery of the portion sandwiched between the bearing 2B and the movable sheave 22 of the second pulley 20 on the other end side of the second shaft 2 so as to be relatively rotatable. A thrust bearing 72 is interposed between the outer end surface of the pressing collar 71 and the end surface of the pressing collar 71 opposite to the outer end surface, and a ball screw groove 71A screwed on the outer periphery of the pressing collar 71 is inserted into the driven gear 73 via a ball (not shown). A ball screw groove (not shown) screwed on the inner periphery is screwed, and the driven gear 73 is supported by a bearing 74 so as to be rotatable and axially immovable. The speed change operation means 60 has a drive gear 75 provided at one end of a speed change operation shaft 60S driven by an electric motor meshed with the driven gear 73 described above.

  The shift operation means 60 is not limited to an electric / mechanical operation means such as an electric motor, but may be a manual operation means such as manually driving the shift operation shaft 60S.

  Thus, when the speed change operation shaft 60S is installed at a rotation angle position that makes it possible to realize a desired speed change ratio between the first shaft 1 and the second shaft 2 by rotation angle control applied to the electric motor, (i) The press collar 61 and the movable sheave 12 of the first pulley 10 backed up by a thrust bearing 62 through the engagement of the drive gear 65 and the driven gear 63 correspond to the rotational angle position. It is set to an axial position, and the effective diameter R1 of the first pulley 10 with respect to the first ring 30 is changed by changing the interval between the sheave surface 11A of the fixed sheave 11 and the sheave surface 12A of the movable sheave 12, and the groove width of the V-groove 13. At the same time that the radius of contact of the sheave surfaces 11A and 12A of the first pulley 10 with the winding member 50 is changed (ii) through the meshing of the drive gear 75 and the driven gear 73, the pressing collar 7 The movable sheave 22 of the second pulley 20 backed up by the pressing collar 71 via the thrust bearing 72 is set to the axial position corresponding to the rotational angle position, and the sheave surface 21A of the fixed sheave 21 and the movable sheave 21 The effective diameter R2 of the second pulley 20 with respect to the second ring 40 (with the winding member 50 on the sheave surfaces 21A and 22A of the second pulley 20) is changed. Change the radius of contact). At this time, the first pulley 10 and the second pulley 20 have the sheaves 11 and 12 and the sheaves 21 and 22 set to have the same size and shape. Further, the speed change operation means 60 sets the pressing collar 61, the driven gear 63, the driving gear 65 and the pressing collar 71, the driven gear 73, and the driving gear 75 to the same shape. Thereby, the direction of the ball screw on the first shaft 1 side (ball screw groove 61A etc. of the pressing collar 61) and the direction of the ball screw on the second shaft 2 side (ball screw groove 71A etc. on the pressing collar 71) are changed. If the distance between the sheave surface 11A of the fixed sheave 11 and the sheave surface 12A of the movable sheave 12 in the first pulley 10 is increased (or reduced) by the speed change operation means 60, the same amount of the fixed sheave 21 in the second pulley 20 is set. The interval between the sheave surface 21A and the sheave surface 22A of the movable sheave 22 is reduced (or enlarged). That is, the speed change operation means 60 is changed and adjusted so that the effective diameter R2 of the second pulley 20 is relatively reduced (or enlarged) in synchronization with the effective diameter R1 of the first pulley 10 being enlarged (or reduced). The rotational speed N2 of the second shaft 2 is increased (or decelerated) as compared with the rotational speed N1 of the first shaft 1, thereby realizing a predetermined speed ratio N2 = (R1 / R2) · N1.

Therefore, according to the present embodiment, the following operational effects can be obtained.
(a) The first ring 30 and the second ring 40 are pressed against the first pulley 10 and the second pulley 20 by the initial tension T and the transmission force W acting on the winding member 50 as shown in FIG. Then, power is transmitted by the traction drive effect based on the contact pressure acting on the contact point P or the friction drive effect. As a result, the rotational input applied to the first shaft 1 is transmitted to the second shaft 2 via the first pulley 10, the first ring 30, the winding member 50, the second ring 40, and the second pulley 20. It is taken out from the two shafts 2 as a rotational output.

  (b) When power is not transmitted (including when idling), as shown in FIG. 3A, the winding member 50 wound around the first ring 30 sandwiched between the first pulleys 10 includes: The same initial tension T acts on both the tension side and the loose side, and the first ring 30 is pressed against the sheave surfaces 11A and 12A of the sheaves 11 and 12 of the first pulley 10 at one contact point P by both tensions T and T. It is done. At this time, in the first ring 30, the moment Ma exerted on the tension side winding member 50 around the contact point P and the tension T acting on the loose side winding member 50 are affected by the contact point P. The moment Mb acting on the surroundings is balanced (Ma = Mb) and is stabilized in a specific posture (in this specific posture, straight lines hanging from the contact point P to the tension-side winding member 50 and the loose-side winding member 50, respectively. When La is L and Lb, Ma = T · La and Mb = T · Lb, and La = Lb from Ma = Mb).

  At this time, similarly, the second ring 40 is also stabilized in a specific posture.

  (c) Next, when the rotational input F is applied to the first shaft 1 and power is transmitted, it is wound around the first ring 30 sandwiched between the first pulleys 10 as shown in FIG. In the winding member 50, the resultant tension of the initial tension T and the transmission force W acts on the tension side, and only the initial tension T acts on the loose side, and the first ring 30 pulled by the transmission force W has the first ring 30. The contact point P with the pulley 10 rolls around the first shaft 1 and moves in the direction opposite to the rotation input F. At this time, the first ring 30 has a moment Ma exerted around the contact point P by the resultant force T and the transmission force W acting on the tension-side winding member 50 and a tension acting on the loose-side winding member 50. The moment Mb exerted around the contact point P by the balance T (Ma = Mb) is again pressed against the sheave surfaces 11A, 12A of the sheaves 11, 12 in the first pulley 10 at the one contact point P. Stabilize (In this specific posture, when the lengths of the straight lines hanging from the contact point P to each of the tension member 50 and the slack member 50 are La and Lb, Ma = (T + W) La, Mb = T · Lb, and since Ma = Mb, La = T · Lb / (T + W)).

  At this time, similarly, the second ring 40 is again stabilized in the specific posture.

  (d) From the above (a) and (b), the first ring 30 and the second ring 40 always have the tension T and the transmission force W both when the power is not transmitted and when the power is transmitted. In a specific posture that is uniquely determined, the sheave surfaces 11A and 12A of both sheaves 11 and 12 in the first pulley 10 or the second pulley 20 are pressed against the sheave surfaces 21A and 22A of both sheaves 21 and 22 to be stabilized. There is no need for a guide roller or the like for stably holding the posture of each ring 30, 40.

  (e) As described in (d) above, the first ring 30 and the second ring 40 are always uniquely determined by the tension T and the transmission force W, both when power is not transmitted and when power is transmitted. The first shaft 10 is stabilized by being pressed against the sheave surfaces 11A and 12A of the sheaves 11 and 12 and the sheave surfaces 21A and 22A of the sheaves 21 and 22 in the first pulley 10 or the second pulley 20 in a fixed specific posture. The power can be transmitted not only in the forward rotation operation of 1 but also in the reverse rotation operation of the first shaft 1 or the operation to which the rotation input (engine brake or the like) is applied from the second shaft 2.

  (f) The rigid first ring 30 and the first ring 30 between the sheave surfaces 11A, 12A or 21A, 22A in which the distance between the sheaves 11, 12 or 21, 22 in each of the first pulley 10 and the second pulley 20 is increased or reduced. The two rings 40 are sandwiched and the rings 30 and 40 are moved in the radial direction of the pulleys 10 and 20 at the time of shifting, and the structure and production of the rings 30 and 40 are simplified.

  (g) As described in (c) above, when the rotational input F is applied to the first shaft 1 and power is transmitted, the first ring 30 has a contact point P with the first pulley 10 at the center of the first shaft 1. To move in the opposite direction to the rotational input F. In other words, the center O1 of the first ring 30 rolls around the first shaft 1 and moves in the direction opposite to the rotation input F. At this time, the center O2 of the second ring 40 rolls around the second shaft 2 and moves in the same direction as the rotational output G. The movement of the center O1 of the first ring 30 and the center O2 of the second ring 40 means that the distance (span) between the centers of the rings 30 and 40 increases (both rings when power is not transmitted). The centers O1 and O2 of 30 and 40 are on a straight line connecting the centers of the first shaft 1 and the second shaft 2, and the span is defined as So (FIG. 4A). The centers O1 and O2 of the rings 30 and 40 are moved in the above-mentioned direction around the first shaft 1 and the second shaft 2, and the span is set to Sw (So <Sw) (FIG. 4B). )).

  That is, the span of the first ring 30 and the second ring 40 is increased, and as a result, the winding member 50 wound around both the rings 30 and 40 is elastically stretched to increase its tension. Therefore, during power transmission, a tension corresponding to the increase in the transmission force W is generated in the winding member 50, and this tension causes the first ring 30 and the second ring 40 to pass through the sheave surfaces 11 and 12 of the first pulley 10 and the second pulley. Thus, the pressing force against the 20 sheave surfaces 21 and 22 is automatically increased, and the sliding of both the rings 30 and 40 is prevented.

  Accordingly, the first ring 30 and the second ring 40 are prevented from slipping with respect to the sheave surfaces 11A, 12A or 21A, 22A of the first pulley 10 and the second pulley 20 when the transmission force is increased. There is no need to intentionally adjust the distance between the sheave surfaces 11A, 12A or 21A, 22A of the pulley 10 and the second pulley 20. It is only necessary to adjust the distance between the sheave surfaces 11A, 12A or 21A, 22A of the first pulley 10 and the second pulley 20 in order to achieve a desired gear ratio between the first shaft 1 and the second shaft 2. Thus, a continuously variable transmission with excellent operability can be constructed.

  (h) Since the first ring 30 and the second ring 40 are made of a rigid body, the force that each ring 30, 40 bites into each pulley 10, 20 on the tension side becomes the force that causes the loose side to separate from each pulley 10, 20, Even if each sheave angle of the first pulley 10 and the second pulley 20 is reduced, there is no possibility that each ring is entangled with each pulley and does not easily come off. Accordingly, each sheave angle θ of the first pulley 10 and the second pulley 20 is reduced, and as a result, each sheave surface 11A, 12A or 21A of the first pulley 10 and the second pulley 20 to obtain a required shift width, It is possible to reduce the interval adjustment amount of 22A, shorten the speed change operation time, and narrow the speed change operation space.

  The embodiment of the present invention has been described in detail with reference to the drawings. However, the specific configuration of the present invention is not limited to this embodiment, and even if there is a design change or the like without departing from the gist of the present invention. It is included in the present invention.

  According to the present invention, a continuously variable transmission that is simple, compact, and excellent in operability can be provided.

DESCRIPTION OF SYMBOLS 1 1st axis | shaft 2 2nd axis | shaft 1 1st pulley 11 Fixed sheave 12 Movable sheave 11A, 12A Sheave surface 13 V groove 20 2nd ring 21 Fixed sheave 22 Movable sheave 21A, 22A Sheave surface 23 V groove 30 1st ring 31, 32 Power transmission surface 33 Gear surface 40 Second rings 41 and 42 Power transmission surface 43 Gear surface 50 Wrapping member 60 Shifting operation means 100 Continuously variable transmission

Claims (3)

In a continuously variable transmission that continuously changes the rotation speed ratio between the first shaft and the second shaft,
A first pulley having a pair of opposed sheaves attached to the first shaft so as to be able to rotate along with the first sheave, and the interval between the sheave surfaces of both sheaves being adjustable;
A second pulley having a pair of opposed sheaves attached to the second shaft so as to be able to rotate along with the second shaft, wherein the distance between the sheave surfaces of both sheaves is adjustable;
A first ring sandwiched between sheave surfaces of both sheaves in the first pulley;
A second ring sandwiched between sheave surfaces of both sheaves in the second pulley;
A continuously variable transmission comprising a winding member wound around a first ring and a second ring. The pair of sheaves of the first pulley includes a fixed sheave and a movable sheave that moves in an axial direction with respect to the fixed sheave, and both sheaves have tapered sheave surfaces that are inclined in opposite directions,
The pair of sheaves of the second pulley includes a fixed sheave and a movable sheave that moves in an axial direction with respect to the fixed sheave, and both sheaves have tapered sheave surfaces that are inclined in opposite directions. Continuously variable transmission.   The said 1st ring and a 2nd ring consist of a ring provided with the gearwheel surface in those outer periphery, and a winding member consists of a toothed winding member wound around a 1st ring and a 2nd ring without slipping. 2. The continuously variable transmission according to 2.

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