JP6360806B2 - Friction type continuously variable transmission - Google Patents

Description

  The present invention relates to a transmission that transmits power by frictional contact and continuously changes a gear ratio.

As a transmission, a friction type continuously variable transmission that transmits power by frictional contact is known.
For example, in Patent Document 1, as a friction-type continuously variable transmission, a pair of large-diameter friction disks supported so as to be movable in the axial direction on one of two orthogonal axes, and the other A pair of small-diameter friction disks that are supported so as to be movable in the axial direction and are clamped by the pair of large-diameter friction disks, and a moving mechanism that moves the movable small-diameter friction disks in the axial direction. A power transmission shaft for transmitting rotational power to each of one large diameter friction disk and a movable small diameter friction disk is proposed.

In this friction type continuously variable transmission, a pair of small-diameter friction disks are clamped by a pair of large-diameter friction disks, so that a movable small-diameter friction disk and a large-diameter friction disk coupled to a power transmission shaft are in frictional contact. Thus, rotational power is transmitted. At this time, when the axial position of the movable small-diameter friction disk is changed by the moving mechanism, the position where the movable small-diameter friction disk is in frictional contact with the large-diameter friction disk coupled with the power transmission shaft is the position of the large-diameter friction disk. The ratio of the rotational speed of the movable small-diameter friction disk is changed in the radial direction and the rotational speed of the large-diameter friction disk coupled to the power transmission shaft, that is, the gear ratio is changed.
Such a friction type continuously variable transmission is disclosed in Patent Document 1, for example.

JP 59-200247 A

However, in a continuously variable transmission as shown in Patent Document 1, a movable small-diameter friction disk is required to secure a speed ratio width (also referred to as “ratio coverage”, hereinafter abbreviated as “recicover”). And a large-diameter friction disk to which a power transmission shaft is coupled, it is necessary to expand the movable range of the position of friction contact, that is, to expand the diameter of a pair of large-diameter friction disks.
As described above, the friction type continuously variable transmission may cause an increase in size in order to secure the reciprocal, and conversely, if the increase in size is suppressed, it may be difficult to secure the reciprocal. .

The present invention was devised in view of the problems as described above, and an object of the present invention is to provide a friction-type continuously variable transmission that can secure a reciprocal cover while suppressing an increase in size. To do.
Note that the present invention is not limited to this purpose, and other effects of the present invention can also be achieved by the functions and effects derived from the respective configurations shown in the embodiments for carrying out the invention which will be described later. Can be positioned as

  (1) In order to achieve the above object, a friction type continuously variable transmission according to the present invention is interposed between a first power transmission shaft and a second power transmission shaft that are coaxially disposed on a main axis. A friction type continuously variable transmission, which is connected to the first power transmission shaft and supported by the first rotating shaft so as not to be relatively rotatable and axially movable; A first disk having a first disk surface frictionally contacting the outer periphery of the first roller and transmitting rotational power to the first roller; and drivingly connected to the first disk, relative to the second rotating shaft A second roller supported so as to be non-rotatable and axially movable; and a second board surface disposed coaxially with the main axis, drivingly connected to the second power transmission shaft, and in frictional contact with an outer periphery of the second roller And a second disk for transmitting rotational power to the second roller. To have.

  (2) The first rotating shaft is disposed coaxially with a first orthogonal axis orthogonal to the main axis, and the first roller is connected to the first power transmission shaft via a first drive connection mechanism. The second rotating shaft is disposed coaxially with a second orthogonal axis orthogonal to the main axis, and the second roller is connected to the first disk via a second drive connection mechanism. preferable.

(3) A plurality of the first rotating shaft and the second rotating shaft are provided radially at equal intervals around the main axis, and each of the plurality of first rotating shafts is equipped with the first roller. Preferably, each of the second rotating shafts is equipped with the second roller.
(4) The first rotating shaft and the second rotating shaft are arranged in parallel with each other so as to form a pair, and the first roller and the second roller are the first disk and the second disk. The first roller and the second roller that are respectively supported by the first rotation shaft and the second rotation shaft that are parallel to each other and rotatably support the first roller and the second roller. It is preferable to provide a housing member that couples the above-mentioned force so as to be transmitted.

(5) The housing member is movably provided along the first rotating shaft and the second rotating shaft, and moves the housing member along the first rotating shaft and the second rotating shaft. It is preferable to provide.
(6) It is preferable to have a torque cam that generates a thrust force in a direction in which the first disk and the second disk are brought close to each other.

(7) The first power transmission shaft is an input shaft to which rotational power is input, the second power transmission shaft is an output shaft from which rotational power is output, and the torque cam is input to the input shaft. It is preferable that the thrust in the direction in which the first disk approaches the second disk is generated by the rotational power generated.
(8) It is preferable that the second disk is provided with a casing that supports the thrust by the torque cam and supports the second disk in a relatively rotatable manner.

(9) The first drive coupling mechanism is disposed coaxially with the main axis and is coupled to the first power transmission shaft in a driving manner, the first rotating shaft, and the first rotation. It is preferable to have a second bevel gear that is coaxially fixed to the shaft and is arranged on the outer peripheral side of the first roller with respect to the main axis while meshing with the first bevel gear.
(10) The second drive coupling mechanism is disposed coaxially with the main axis, and is fixed to a third rotating shaft coupled to the rotation center of the first disk, A second rotating shaft, and a fourth bevel gear fixed on the same axis as the second rotating shaft and arranged on the inner peripheral side of the second roller with respect to the main axis while meshing with the third bevel gear It is preferable to have.

According to the friction type continuously variable transmission according to the present invention, the ratio between the rotational speed of the first roller and the rotational speed of the first disk (hereinafter referred to as “first speed ratio”) according to the axial position of the first roller. And the ratio between the rotational speed of the second roller and the rotational speed of the second disk (hereinafter referred to as “second gear ratio”) is variable according to the axial position of the second roller. Set to
For this reason, the ratio between the rotational speed of the first power transmission shaft and the rotational speed of the second power transmission shaft according to the friction type continuously variable transmission of the present invention, that is, the gear ratio by the friction type continuously variable transmission is This corresponds to the product of the gear ratio and the second gear ratio.
As described above, in the friction type continuously variable transmission according to the present invention, the transmission ratio can be changed in a power manner without increasing the diameter of each disk. it can.

1 is a cross-sectional view schematically showing an entire friction type continuously variable transmission according to an embodiment of the present invention. It is an expanded sectional view showing typically the principal part of the friction type continuously variable transmission concerning one embodiment of the present invention. It is a single figure which takes out and shows an input part in a torque cam of a friction type continuously variable transmission concerning one embodiment of the present invention, (a) corresponds to an AA arrow of Drawing 1, and (b) is (a). ) In the direction of arrows B-B. A first roller, a first disk, a first bevel gear, a second bevel gear, a first rotation shaft, a third rotation shaft, and a first central structure of a friction continuously variable transmission according to an embodiment of the present invention. It is a figure taken out and is a figure corresponding to CC arrow of FIG. It is a typical perspective view showing the circumference of the 1st roller and the 2nd roller of the friction type continuously variable transmission concerning one embodiment of the present invention.

Embodiments of the present invention will be described below with reference to the drawings.
The friction type continuously variable transmission according to the present invention is a transmission that transmits power by frictional contact and continuously (steplessly) changes the gear ratio. The friction type continuously variable transmission can be mounted on various vehicles such as an automobile and a motorcycle.
This friction type continuously variable transmission continuously and variably changes the gear ratio in a plurality of stages. In the following description, a friction type continuously variable transmission in which the gear ratio is continuously and variably changed in two stages will be described as an example.

  In this embodiment, the main axis and two orthogonal axes orthogonal to the main axis are used as a reference. Of the two orthogonal axes, the input-side (one) axis is the input-side axis (first orthogonal axis), and the output-side (the other) axis is the output-side axis (second orthogonal axis). Further, the inside and the outside are determined based on the main axis or the orthogonal axis, and the upstream and the downstream are determined based on the transmission direction of the rotational power.

[One Embodiment]
[1. Constitution]
First, the friction type continuously variable transmission according to the present embodiment will be described with reference to FIG.
The friction type continuously variable transmission shifts the rotational power input to the input shaft (first power transmission shaft) 1 and outputs it to the output shaft (second power transmission shaft) 2. These input shaft 1 and output shaft 2 are coaxially arranged on the main axis C ₁ .
This friction continuously variable transmission is interposed between an input shaft 1 and an output shaft 2.

  The friction type continuously variable transmission includes a first drive coupling mechanism 10, a first roller 30, a first disk 40, a second coupling drive mechanism 20, a second roller 50, and a second disk 60 in the order in which the rotational power is transmitted. Is provided.

The first roller 30 is coupled to the input shaft 1 via the first coupling drive mechanism 10. The first roller 30 is provided such that it cannot rotate relative to the first rotating shaft 17 and is movable in the axial direction (for example, the direction along the input-side axis C ₁₁ ).
As shown in FIG. 2, the first disk 40 has a first disk surface 40 a that frictionally contacts the outer periphery 30 a of the first roller 30. The first disc surface 40a of the first disc 40 and the outer periphery of the first roller 30 are in frictional contact with each other, so that rotational power can be transmitted to each other.

  As the first roller 30 moves in the axial direction of the first rotating shaft 17, the position of friction contact between the first roller 30 and the first disk 40 is changed, and the rotational speed of the first roller 30 and the first disk 40 are changed. The first speed ratio, which is the ratio to the rotational speed of is set to be variable. In this way, the first stage of continuous variable transmission is performed.

The second roller 50 is connected to the first disk 40 via the second connection drive mechanism 20. The second roller 50 is provided so as not to rotate relative to the second rotating shaft 24 and to be movable in the axial direction (for example, the direction along the output-side axis C ₂₁ ).
The second disk 60 has a second disk surface 60 a that frictionally contacts the outer periphery of the second roller 50. When the second disk surface 60a of the second disk 60 and the outer periphery 50a of the second roller 50 are in frictional contact, each other's rotational power can be transmitted.

  When the second roller 50 moves in the axial direction of the second rotating shaft 24, the position where the second roller 50 and the second disk 60 make frictional contact is changed, and the rotational speed of the second roller 50 and the second disk 60 are changed. The second speed ratio, which is a ratio to the rotational speed of, is variably set. In this way, the second stage of continuous variable transmission is performed.

In the present embodiment, a friction type continuously variable transmission that synchronizes the first-stage continuous variable transmission and the second-stage continuous variable transmission will be described as an example. For this reason, in the friction type continuously variable transmission, the first roller 30 and the second roller 50 are provided between the first disk 40 and the second disk 60, and the first roller 30 and the second roller 50 are connected to each other. A housing member 70 to be supported and an actuator mechanism 80 (see FIG. 1) for moving the housing member 70 are provided.
Hereinafter, each configuration of the friction type continuously variable transmission will be described in the order of the transmission direction of the rotational power, and then the housing member 70 and the actuator mechanism 80 will be described.

[1-1. Input axis]
As shown in FIG. 1, the input shaft 1 is a power transmission shaft to which rotational power from a drive source such as an engine or an electric motor (also simply referred to as “motor”) is input. The input shaft 1 receives rotation around the main axis C ₁ . FIG. 1 shows an example in which a rotor 99 rotating with respect to a stator (not shown) is fixed to the input shaft 1.

The input shaft 1 is formed as a hollow shaft in which a coaxial support member 8 is inserted. The support member 8 is fixed to the casing 9.
A first connection drive mechanism 10 described below is connected to the downstream side of the input shaft 1 in the power transmission direction.

[1-2. First drive coupling mechanism]
The first coupling drive mechanism 10 is a mechanism that bears power transmission between the input shaft 1 and the first roller 30. The first coupling drive mechanism 10 includes an input unit 12, a torque cam 11, an output unit 14, a first bevel gear 15, a second bevel gear 16, and a first rotation shaft 17 in the order of transmission of rotational power.
Input unit 12 on the upstream side in the power transmission direction, the output unit 14 and the first bevel gear 15 is arranged on the main axis C ₁ and coaxially, respectively.

On the other hand, as shown in FIG. 4, a plurality (three in each case) of the second bevel gear 16 and the first rotating shaft 17 on the downstream side in the power transmission direction are provided. The second bevel gear 16 and the first rotating shaft 17 are arranged coaxially with the input side axes C ₁₁ , C ₁₂ , and C ₁₃ that are orthogonal to the main axis C ₁ . Further, a plurality of first rotating shafts 17 are provided radially at equal intervals around the main axis C ₁ corresponding to each of the second bevel gears 16.

The second bevel gear 16 and the first rotating shaft 17 are configured in the same manner except for the arrangement location (the positions of the input side axes C _{11 to} C ₁₃ ). Here, a description will be given by focusing on what is provided coaxially with the input-side axis C ₁₁ .
FIG. 4 shows an example in which three first rotating shafts 17 are provided corresponding to the three second bevel gears 16. However, the number of each of the second bevel gear 16 and the first rotating shaft 17 may be two or four or more, and is set by the magnitude of the transmission torque and the magnitude of the thrust by the torque cam 11 described above. It is preferable.

[1-2-1. Input section and output section]
As shown in FIG. 1, the input unit 12 is a part that transmits and inputs rotational power from the input shaft 1 to the torque cam 11. The input unit 12 is fixed on the downstream side of the input shaft 1 in the power transmission direction. Here, the input portion 12 into which the coaxial support member 8 is inserted through a bearing is formed in a hollow flange shape.
As shown in FIG. 2, the input unit 12 has an input surface 12a that extends along a plane perpendicular to the main axis C ₁ in the power transmission direction downstream side.

The output unit 14 is a part where rotational power and thrust are output from the torque cam 11. The output unit 14 has an output surface 14a which is arranged to be input unit 12 and the relative rotation, extending along a plane perpendicular to the main axis C ₁ in the power transmission direction upstream side. The output surface 14a faces the input surface 12a of the input unit 12 with a space. These surfaces 12a and 14a are provided with cam grooves 12b and 14b for accommodating the rolling elements 13 at corresponding locations, respectively.
Here, a coaxial support member 8 is inserted into the output portion 14 via a bearing. The output unit 14 is formed in a disk shape. A first bevel gear 15, which will be described in detail later, is fixed on the downstream side of the output unit 14 in the power transmission direction.

[1-2-2. Torque cam]
The torque cam 11 is a mechanism that generates thrust by the rotational power of the input shaft 1. The thrust here is a force in a direction in which the first disk 40 and the second disk 60 are brought close to each other. Here, a torque cam that generates a thrust force that presses the first disk 40 in a direction along the main axis C ₁ and from the input shaft 1 toward the output shaft 2 (a direction in which the first disk 40 approaches the second disk 60). 11 will be described as an example.

The torque cam 11 includes the cam grooves 12b and 14b described above and a rolling element 13 interposed between the cam grooves 12b and 14b.
As shown in FIG. 3A, the input surface 12a is formed with a plurality of input cam grooves 12b (signs are attached to only one portion) at equal intervals along the circumferential direction.
3A illustrates an example in which the input portion 12 is provided with four input cam grooves 12b. However, the number of input cam grooves 12b may be three or less. It may be 5 or more, and is preferably set according to the magnitude of the transmission torque.

  As shown in FIG. 3B, the input cam groove 12b is formed so as to gradually become shallower from the deepest portion 12c in the circumferential direction toward both directions of the rotation direction and the reverse rotation direction (that is, the circumferential direction). Yes. In FIGS. 3A and 3B, the rotation direction of the input unit 12 is illustrated by a double arrow, but this rotation direction may be opposite.

Similarly, a plurality of output cam grooves 14b are formed on the output surface 14a of the output portion 14 along the circumferential direction. Each output cam groove 14b is provided corresponding to each input cam groove 12b of the input surface 12a, and gradually becomes shallower from the deepest portion 14c in the circumferential direction toward the direction along the rotation direction and the reverse rotation direction. Is formed.
The rolling element 13 is housed in the input cam groove 12b at the upstream side in the power transmission direction (denoted by reference numeral “13a”), and the output cam groove at the downstream side in the direction of power transmission (denoted by reference numeral “13b”). 14b. In addition, the rolling element 13 is formed in a spherical shape.

[1-2-3. First bevel gear and second bevel gear]
Next, the first bevel gear 15 and the second bevel gear 16 will be described with reference to FIGS. 2 and 4.
The first bevel gear 15 and the second bevel gear 16 (signs are attached to only one place) convert rotation around the main axis C ₁ into rotation around the input side axis C ₁₁ . The rotation around the main axis C ₁ is transmitted from the output portion 14 of the torque cam 11 to the first bevel gear 15, and the rotation around the input side axis C ₁₁ is transmitted from the second bevel gear 16 to the first rotation shaft 17 (only one place is indicated by a sign). Will be output.

The first bevel gear 15 rotates about the main axis C ₁ . The first bevel gear 15 is fixed in an annular shape on the outer periphery of the output portion 14 of the torque cam 11.
Teeth 15a of the first bevel gear 15, (both see FIG. 1) the output shaft 2 from the outer periphery of the output portion 14 in a direction along the main axis C ₁ of the input shaft 1 is provided so as to protrude toward the .

As shown in FIG. 4, a plurality of second bevel gears 16 are provided at equal intervals along the circumferential direction around the main axis C ₁ . These second bevel gears 16 are configured in the same manner except for the arrangement location. Here, a description will be given by focusing on what is provided coaxially with the input-side axis C ₁₁ .

The second bevel gear 16, and rotates about an input axis C _11. The second bevel gear 16 is provided closer to the output shaft 2 than the first bevel gear 15. The teeth 16 a of the second bevel gear 16 mesh with the teeth 15 a of the first bevel gear 15.
In the present embodiment, an example in which a bevel gear is used as the first coupling drive mechanism 10 is shown, but it goes without saying that other types of gears such as a spur gear can be used instead of the bevel gear.
Each second bevel gear 16 is fixed to a first rotating shaft 17 described below.

[1-2-4. First rotation axis]
The first rotary shaft 17, and rotates about an input axis C _11. As shown in FIGS. 2 and 4, the first rotating shaft 17 has an end portion (hereinafter referred to as “inner peripheral side end portion”) 17 a close to the main axis C ₁ in the housing 9 (see FIG. 2). The first center structure 7a is fixedly supported via a bearing. On the other hand, an end portion (hereinafter referred to as “outer end portion”) 17b opposite to the inner peripheral end portion 17a of the first rotating shaft 17 is a bearing on the side wall portion 9b of the housing 9 as shown in FIG. Is supported through.

  As shown in FIGS. 2 and 4, the first rotating shaft 17 is formed with a spline groove 17 c on the inner peripheral side end portion 17 a side than the fixed first bevel gear 16. A first roller 30 described below is supported in the spline groove 17c.

[1-3. First roller]
As shown in FIG. 4, a plurality of first rollers 30 (signs are attached to only one place) are provided corresponding to each of the first rotating shafts 17. Each of these first rollers 30 is configured in the same manner except for the arrangement location. Here, a description will be given by focusing on what is provided coaxially with the input-side axis C ₁₁ .

The first roller 30 is adapted to rotate about the input axis C _11. As shown in FIGS. 4 and 5, the first roller 30 is fitted with the spline shaft 17 c of the first rotating shaft 17 so as to rotate integrally, and is movable along the input-side axis C _11. Yes.

As described above, the second bevel gear 16, the first roller 30, and the first rotating shaft 17 are arranged with the input side axis C ₁₁ as the rotation center, and the first rotating shaft 17 has the main axis C ₁ . As a reference, the first roller 30 is fixed on the inner peripheral side of the second bevel gear 16.
As shown in FIG. 2, the outer periphery 30a of the first roller 30 is in frictional contact with the first disk surface 40a of the first disk 40 described below.

[1-4. First disc]
The first disc 40 is to rotate about the main axis C _1. The first disk 40 has a first disk surface 40a on the output shaft 2 side and a first back surface 40b on the input shaft 1 side. These first board 40a and the first rear 40b extends along a plane perpendicular to the main axis C _1, respectively.

The first disc 40 is disposed on a side (inner peripheral side) close to the main axis C ₁ than the first bevel gear 15 and the second bevel gear 16 in a direction perpendicular to the main axis C _1, the main axis C ₁ is disposed between the output portion 14 of the torque cam 11 and the first roller 30 in the direction along ₁ .

The first disk 40 and the output unit 14 are provided so as to be capable of relative rotation, and are disposed so as to be able to transmit a force in a direction along the main axis C ₁ . Specifically, the first back surface 40b of the first disk 40 and a surface 14c opposite to the output cam surface 14a of the output unit 14 (hereinafter referred to as “output unit back surface”) are arranged to face each other. A bearing is interposed between the first back surface 40b and the output unit back surface 14c.
A second drive coupling mechanism 20 described below is coupled to the rotation center portion 40c of the first disk 40.

[1-5. Second drive coupling mechanism]
The second connection drive mechanism 20 is a mechanism that bears power transmission between the first disk 40 and the second roller 50.
As shown in FIG. 1, the second coupling drive mechanism 20 includes a third rotation shaft 21, a third bevel gear 22, a fourth bevel gear 23, and a second rotation shaft 24 in the order of the transmission direction of the rotational power.
The third rotating shaft 21 and the third bevel gear 22 on the upstream side in the power transmission direction are arranged coaxially with the main axis C ₁ .

On the other hand, the fourth bevel gear 23 and the second rotation shaft 24 on the downstream side in the power transmission direction are respectively provided in a plurality (three in each case), like the second bevel gear 16 and the first rotation shaft 17. . Each of the fourth bevel gear 23 and the second rotating shaft 24 is disposed coaxially with the output-side axis C ₂₁ (C ₂₂ , C ₂₃ ) orthogonal to the main axis C ₁ . A plurality of second rotating shafts 24 are provided radially at equal intervals around the main axis C ₁ corresponding to each of the fourth bevel gears 23.

The second rotating shaft 24 and the corresponding first rotating shaft 17 overlap when viewed along the main axis C ₁ (for example, when projected onto the first disk surface 40a of the first disk 40). It is arranged like this. In other words, the first rotating shaft 17 and the second rotating shaft 24 are arranged in parallel with each other so as to form a pair.
The fourth bevel gear 23 and the second rotating shaft 24 are configured in the same manner except for the arrangement location (positions of the output side axes C _{21 to} C ₂₃ ). Here, a description will be given by focusing on what is provided coaxially with the output-side axis C ₂₁ .

[1-5-1. Third rotation axis]
The third rotating shaft 21, and rotates about the main axis C _1. As shown in FIG. 2, the third rotating shaft 21 has an input shaft 1 (see FIG. 1) side end (hereinafter referred to as “input side end”) 21 a that can rotate on the support member 8 via a bearing. The output shaft 2 (see FIG. 1) side end portion (hereinafter referred to as “output side end portion”) 21b is supported by the second central structure 7b fixed to the housing 9 via a bearing. ing.

  A rotation center portion 40c of the first disk 40 is fixed on the upstream side in the power transmission direction of the third rotating shaft 21, that is, on the input shaft 1 side. On the other hand, a third bevel gear 22 described below is fixed on the downstream side in the power transmission direction of the third rotating shaft 21, that is, on the output shaft 2 side.

[1-5-2. Third bevel gear and fourth bevel gear]
The third bevel gear 22 and the fourth bevel gear 23 convert rotation around the main axis C ₁ into rotation around the output side axis C ₂₁ . The rotation around the main axis C ₁ is transmitted from the third rotation shaft 21 to the third bevel gear 22, and the rotation around the output side axis C ₂₁ is output from the fourth bevel gear 23 to the second rotation shaft 24.

The third bevel gear 22 rotates about the main axis C ₁ . On the other hand, the fourth bevel gear 23 is to rotate about the output-side axis C _21.
The teeth 22a of the third bevel gear 22 and the teeth 23a of the fourth bevel gear 23 mesh with each other. The fourth bevel gear 23 is fixed to a second rotating shaft 24 described below.

[1-5-3. Second rotation axis]
The second rotary shaft 24, and rotates about the output-side axis C _21. The second rotary shaft 24, the end near the main axis C ₁ side (hereinafter, referred to as "inner end portion") 24a is supported through a bearing on the second central structure 7b, an inner peripheral side An end portion (hereinafter referred to as “outer end portion”) 24b opposite to the end portion 24a is supported on the side wall portion 9b of the housing 9 via a bearing.

  A spline groove 24 c is formed on the second rotating shaft 24 on the outer peripheral side end portion 24 b side of the fourth bevel gear 23 that is fixed. A second roller 50 described below is supported in the spline groove 24c.

[1-6. Second roller]
Although not shown, the second roller 50 is provided corresponding to each of the second rotating shafts 24. These second rollers 50 are configured in the same manner except for the locations where they are disposed. Here, a description will be given by focusing on what is provided coaxially with the output-side axis C ₂₁ .
The second roller 50, and rotates about the output-side axis C _21. The second roller 50, as shown in FIGS. 2 and 5, are fitted with a spline groove 24c of the second rotary shaft 24 is movable along the output-side axis C ₂₁ with integrally rotated Yes.

As shown in FIG. 2, the second roller 50 coaxial with the output-side axis C ₂₁ is viewed along the main axis C ₁ (for example, when projected onto the first disk surface 40a of the first disk 40). The first roller 30 is coaxial with the input side axis C ₁₁ connected by a housing member 70, which will be described in detail later. In other words, the corresponding first roller 30 and second roller 50 are arranged such that the radial position and the circumferential position with respect to the main axis C ₁ coincide with each other.

Thus, the fourth bevel gear 23, second roller 50 and the second rotary shaft 24 is disposed as the rotation about the output-side axis C _21, The second rotating shaft 24, the main axis C ₁ As a reference, the second roller 50 is fixed on the outer peripheral side of the fourth bevel gear 23.
The outer periphery 50a of the second roller 50 is in frictional contact with a second disk surface 60a of a second disk 60 described below.

[1-7. Second disc and output shaft]
The second disc 60 is to rotate about the main axis C _1. The second disk 60 has a first disk surface 60a on the input shaft 1 (see FIG. 1) side and a second back surface 60b on the output shaft 2 (see FIG. 1) side. These second board 60a and the second rear 60b extends along a plane perpendicular to the main axis C _1, respectively.

  Further, the second disk 60 is supported by the casing 9 so as to be able to counter the thrust by the torque cam 11 and to be relatively rotatable. Specifically, the second back surface 60b of the second disk 60 and the inner wall surface 91a of the output side wall portion 9a of the housing 9 are arranged to face each other, and a bearing is provided between the second back surface 60b and the inner wall surface 91a. Is intervening.

As shown in FIG. 1, the output shaft 2 is connected to the rotation center portion 60 c of the second disk 60.
The output shaft 2 is a power transmission shaft that outputs the rotational power of the second disk 60. The output shaft 2 outputs rotation about the main axis C ₁ .
Here, the output shaft 2 is supported by the casing 9 via a bearing.

[1-8. Housing member]
Next, the housing member 70 will be described with reference to FIGS. 2 and 5.
The housing member 70 rotatably supports the first roller 30 and the second roller 50 that are respectively supported by the first rotation shaft 17 and the second rotation shaft 24 that are parallel to each other, and in the direction along the main axis C ₁ . The force is connected so that it can be transmitted. The housing member 70 is provided so as to be movable along the first rotating shaft 17 and the second rotating shaft 24. One housing member 70 is provided for one first roller 30 and one second roller 50 corresponding thereto. For example, for the first roller 30 movable along the input side axis C ₁₁ (C ₁₂ , C ₁₃ ) and the second roller 50 movable along the output side axis C ₂₁ (C ₂₂ , C ₂₃ ). One housing member 70 is provided.

Although not shown, three housing members 70 are provided corresponding to the three sets of rollers 30 and 50 here. These housing members 70 are configured in the same manner except for an arrangement location. Here, a description will be given focusing on the housing member 70 movable along the input side axis C ₁₁ and the output side axis C ₂₁ .

The housing member 70 is coupled in a direction along a first roller 30 and second roller 50 to the main axis C _1. The housing member 70 supports the first roller 30 via a bearing 71 and similarly supports the second roller 50 via a bearing 72.
In the housing member 70, a female screw hole 70 a is provided between the first roller 30 and the second roller 50 (center). As shown in FIG. 1, an actuator mechanism 80 is connected to the female screw hole 70a.

[1-9. Actuator mechanism]
Finally, the actuator mechanism 80 will be described with reference to FIGS.
The actuator mechanism 80 moves the housing member 70 in a direction along the first rotating shaft 17 and the second rotating shaft 24.
As shown in FIG. 1, the actuator mechanism 80 includes a motor 81, and the motor 81 is fixed to the side wall 9 b (see FIG. 2) of the casing 9.

The output shaft 82 of the motor 81 is provided along the first rotating shaft 17 and the second rotating shaft 24, and a male screw 82a is threaded as shown in FIG. The output shaft 82 projects through the side wall 9 b of the casing 9 and protrudes inside the casing 9. In addition, as shown in FIG. 2, the front-end | tip 82b of the output shaft 82 is supported by the 1st center part structure 7a (refer FIG. 1) via the bearing.
The output shaft 82 is provided through the male screw 82 a so as to be screwed into the female screw hole 70 a of the housing member 70.

A plurality (three in this case) of actuator mechanisms 80 are provided corresponding to the housing members 70, respectively. In these actuator mechanism 80, the rotation of each motor 81 (the rotation of the output shaft 82) is controlled synchronously, the radial position of each housing member 70 (the distance from the main axis C ₁₎ are synchronized. However, the actuator mechanism 80 includes, in addition to one motor 81 and one output shaft 82, a link mechanism that synchronizes and mechanically connects the radial movements of the plurality of housing members 70. The radial position of each housing member 70 may be synchronized by controlling the rotation of the motor 81.
Except for the second disk 60, the members contributing to power transmission, such as the first disk 40, the first and second rotating shafts 17 and 24, and the first and second rollers 30 and 50, generate the thrust of the torque cam 11. in order to transmit to the second disc 60, for example, by adjusting the bearing clearance (so-called backlash or play), it is preferable that along the main axis C ₁ direction is configured only slightly movable.

[2. Action and Effect]
Since the friction type continuously variable transmission according to the embodiment of the present invention is configured as described above, the following operations and effects can be obtained.

[2-1. Action]
First, the operation of the friction type continuously variable transmission according to the present embodiment will be described.
First, the operation will be described focusing on transmission of rotational power.
When rotational power is input and the input shaft 1 rotates, the torque cam 11 rotates at the same rotational speed. In the torque cam 11, the rotation of the input unit 12 fixed to the input shaft 1 rotates the output unit 14 via the rolling element 13. In this way, the input unit 12 and the output unit 14 rotate at the same rotational speed.

When the output portion 14 of the torque cam 11 rotates, the first bevel gear 15 rotates at the same rotational speed, and the second bevel gear 16 that meshes with the first bevel gear 15 rotates. At this time, the rotational power is transmitted toward the input shaft 1 side along the main axis C ₁ to the output shaft 2 side. Further, the rotational power is changed by the ratio between the number of teeth of the first bevel gear 15 (corresponding to the diameter of the first bevel gear 15) and the number of teeth of the second bevel gear 16 (corresponding to the diameter of the second bevel gear 16). The
The second bevel gear 16, the first rotating shaft 17, and the first roller 30 rotate at the same rotational speed.

Next, rotational power is transmitted from the output shaft 2 side to the input shaft 1 side along the main axis C ₁ between the first roller 30 and the first disk 40. At this time, the first speed change is a ratio between the diameter of the first roller 30 and the position where the first roller 30 is in frictional contact with the first disk 40 (the diameter of the portion where the first roller 30 is in frictional contact with the first disk 40). The rotation speed is changed by the ratio.
The first disk 40 that rotates at the rotational speed changed at the first gear ratio rotates integrally with the third rotating shaft 21 and the third bevel gear 22.

The fourth bevel gear 23 meshing with the third bevel gear 22 includes the number of teeth of the third bevel gear 22 (corresponding to the diameter of the third bevel gear 22) and the number of teeth of the fourth bevel gear 23 (of the fourth bevel gear 23). Rotates at a rotational speed that is changed by a ratio of
The fourth bevel gear 23, the third rotating shaft 24, and the second roller rotate at the same rotational speed.

Between the second roller 50 and the second disk 60, the diameter of the second roller 50 and the position where the second roller 50 is in frictional contact with the second disk 60 (the place where the second roller 50 is in frictional contact with the second disk 60). The rotation speed is changed at a second speed ratio that is a ratio of
The second disk 60 rotating at the rotational speed thus shifted transmits the rotational power to the output shaft 2 at the same rotational speed.

When the motor 81 of the actuator mechanism 80 is actuated, the output shaft 82 of the motor 81 rotates, and the housing member 70 having the female screw portion 70a that engages with the male screw 82a of the output shaft 82 becomes the first rotating shaft 17 and the second rotating shaft 17. It moves in the direction along the rotation axis 24. Thus, the radial position of the first roller 30 and second roller 50 (distance from the main axis C ₁₎ is changed synchronously.

For example, the first gear ratio and the second gear ratio when the housing member 70 and the rollers 30 and 50 are moved away from the main axis C ₁ are the same as those of the housing member 70 and the rollers 30 and 50. It is on the Low side with respect to the first gear ratio and the second gear ratio when moved to a position close to C ₁ (indicated by a two-dot chain line in FIGS. 1 and 2). In the friction type continuously variable transmission according to the present embodiment, the former gear ratio corresponds to the high-side first gear ratio and the second gear ratio, respectively, and the latter gear ratio corresponds to the low-side first gear ratio. This corresponds to the product of the ratio and the second transmission ratio.

Next, the operation will be described by paying attention to the thrust by the torque cam 11.
In the torque cam 11, a force that twists in the circumferential direction when the main axis C ₁ is the center acts between the input portion 12 and the output portion 14. Specifically, the rolling element 13 is pressed in the direction along the main axis C ₁ via the input cam groove 12b, and the output portion 14 is pressed in the direction along the main axis C ₁ via the output cam groove 14b. The thrust generated in this way is transmitted from the output unit 14 along the main axis C ₁ in the order of the first disk 40, the first roller 30, the housing member 70, the second roller 50, and the second disk 60.

  Since the second back surface 60b of the second disk 60 is supported by the inner wall surface 91a of the casing 9 via a bearing, the thrust generated by the torque cam 11 is caused by the reaction of the second disk 60 supported by the casing 9. The first and second rollers 30 and 50 act as a compressive force that sandwiches the first and second rollers 30 and 50 between the first and second disks 40 and 60. For this reason, the thrust can also be regarded as a compressive force generated between the first disk 40 and the second disk 60.

[2-2. effect]
Hereinafter, effects of the friction type continuously variable transmission according to the present embodiment will be described.
According to the friction type continuously variable transmission of the present embodiment, the rotational speed of the first roller 30 and the first roller 30 according to the position of the first roller 30 on the input side axis C ₁₁ (distance from the main axis C ₁ ). is first gear ratio is variably set the ratio of the rotational speed of the disc 40, also in accordance with the position on the output side axis C ₂₁ of the second roller 50 (the distance between the main axis C _1), second Since the second gear ratio, which is the ratio between the rotational speed of the roller 50 and the rotational speed of the second disk 60, is variably set, the gear ratio of the friction-type continuously variable transmission is the first gear ratio and the second gear ratio. Corresponds to the product of. As described above, since the two-stage variable speed change mechanism is provided, the speed change ratio can be changed in a power manner, and it is possible to secure the recovery cover while suppressing an increase in size.

Here, the conventional friction type continuously variable transmission provided with the variable transmission mechanism of only one step is compared with the friction type continuously variable transmission of this embodiment.
In a friction type continuously variable transmission equipped with a variable transmission mechanism of only one step, it is necessary to expand a movable range of a roller that is in frictional contact with a disk in order to secure a recovery cover. For this purpose, it is necessary to increase the diameter of the disk, which may increase the size of the friction type continuously variable transmission. If the increase in size is suppressed, the movable range of the roller cannot be expanded, and there is a possibility that the reciprocal cover cannot be secured. On the other hand, since the friction type continuously variable transmission of this embodiment has a two-stage variable transmission mechanism, it is possible to secure a reciprocal cover while suppressing an increase in size.

The first roller 30 and second roller 50 is provided between the first disc 40 and second disc 60, the direction along the main axis C ₁ with the first roller 30 and second roller 50 rotatably supports each because having a housing member 70 for coupling the force to be transmitted, the distance can be synchronized with respect to the main axis C ₁ of the first roller 30 and second roller 50, at the same time changes the first gear ratio and a second gear ratio can do. Furthermore, since the corresponding first roller 30 and second roller 50 are supported by one housing member 70, a simple configuration can be achieved.

  Since the torque cam 11 generates a thrust force in the direction in which the first disk 40 and the second disk 60 are brought close to each other, the first roller 30 and the first disk surface 40a of the first disk 40 are pressed against each other, and the first The location where the two rollers 50 and the second plate surface 60a of the second plate surface 60 are in frictional contact can be pressed. Thereby, the transmission efficiency of rotational power can be improved.

  Further, the torque cam 11 uses the rotational power transmitted in the friction type continuously variable transmission in order to generate thrust in the direction in which the first disk 40 approaches the second disk 60 by the rotational power input to the input shaft 1. Thus, thrust can be generated in a desired direction. Furthermore, a simple configuration can be achieved without using hydraulic pressure, air pressure, or the like to generate thrust. As a result, another drive source for generating thrust can be omitted, and energy efficiency can be improved.

  Since the second disk 60 is supported by the casing 9 so as to be able to counteract the thrust by the torque cam 11 and be relatively rotatable, the second disk 60 is moved from the input shaft 1 side to the output shaft 1 by the thrust generated by the torque cam 11. When pressed to the side, a compressive force can be applied between the first disk 40 and the second disk 60 by the reaction of the thrust. Therefore, the frictional contact portion can be reliably pressed by the thrust, and the power transmission efficiency can be improved.

A plurality of first rotating shafts 17 and second rotating shafts 24 are provided radially at equal intervals around the main axis C _1. Each of the plurality of first rotating shafts 17 is equipped with a first roller 30, and a plurality of second rotating shafts are provided. Since each of the rotation shafts 24 is equipped with the second roller 50, the thrust generated by the torque cam 11 can be shared by each of the first roller 30 and the second roller 50 provided in plurality, and the thrust is generated. Power transmission efficiency can be ensured by acting efficiently.

  Since the actuator mechanism 80 moves the housing member 70 that rotatably supports the rollers 30 and 50 along the first rotating shaft 17 and the second rotating shaft 24, the rollers 30 and 50 can be moved synchronously. The first gear ratio and the second gear ratio can be changed simultaneously. Thereby, a gear ratio can be changed efficiently with a simple configuration. In other words, it is possible to expand the receiver while suppressing an increase in the size of the transmission. For example, the configuration can be simpler than that in which an actuator mechanism is connected to each of the first roller and the second roller.

The first drive coupling mechanism 10 includes a first bevel gear 15 that is coaxial with the main axis C _1, and a second bevel gear 16 that is coaxial with the first rotation shaft 17 disposed along the input-side axis C _11. Therefore, the rotational power around the main axis C ₁ input to the input shaft 1 can be converted to rotational power around the input side axis C ₁₁ and transmitted to the first roller 30.

The second drive coupling mechanism 20 includes a third bevel gear 23 coaxial with the main axis C _1, and a fourth bevel gear 23 coaxial with the second rotation shaft 24 disposed along the output side axis C _21. Therefore, the rotational power around the main axis C ₁ of the first disk 40 can be converted into rotational power around the output side axis C ₂₁ and transmitted to the second roller 50.

Furthermore, the first disc 40 is disposed on a side (inner peripheral side) close to the main axis C ₁ than the first bevel gear 15 and the second bevel gear 16 in a direction perpendicular to the main axis C _1, the main axis C ₁ , the first roller 30 and the second roller 50 are disposed between the first disk 40 and the second disk 60 because the first roller 30 is disposed between the output portion 14 of the torque cam 11 and the first roller 30. The thrust generated by the torque cam 11 acts on both the frictional contact point between the first roller 30 and the first disk 40 and the frictional contact point between the second roller 50 and the second disk 60. Can be made.

[Others]
Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention. Each structure of one Embodiment mentioned above can be selected as needed, and may be combined suitably.

  In the above-described embodiment, the friction type continuously variable transmission having the two-stage variable transmission mechanism is shown. However, the variable transmission mechanism may be provided in three or more stages. For example, a disk having a roller which is relatively rotatable and supported so as to be movable in the axial direction, and a disk surface which is in frictional contact with the outer periphery of the roller is provided between the first roller 30 and the input shaft 1 and the second roller 40. It may be provided between the output shaft 2. That is, an arbitrary number of variable speed change mechanisms may be interposed between the rollers 30 and 50 and the input / output shafts 1 and 2. Thus, it is sufficient that at least the input shaft 1 is drivingly connected to the first roller 30, and the output shaft 2 only needs to be drivingly connected to the second roller 50. In this case, the transmission gear ratio can be changed in a power manner by the number of stages provided with the variable transmission mechanism, and further the recovery cover can be expanded.

  Further, the connection drive mechanisms 10 and 20 are not limited to the above-described configuration, and various drive connection mechanisms can be used. For example, according to the design of the friction type continuously variable transmission, the addition of a further gear mechanism and the arrangement of each component may be changed.

  Further, the housing member 70 may be omitted. In this case, by providing a moving mechanism (for example, an actuator mechanism) that moves the first roller 30 and the second roller 50 along the first rotating shaft 17 and the second rotating shaft 24, respectively, The gear ratio can be changed independently. In this case, instead of the torque cam 11, it is preferable to provide a device that generates contact pressure at each frictional contact location by hydraulic pressure or air pressure. At this time, naturally, the second disk 60 does not need to be supported so as to be able to resist the thrust of the torque cam 11.

  In the embodiment described above, the rotational power is input from the input shaft 1, but conversely, the rotational power may be input from the output shaft 2. In this case, the above input / output relationship may be read in reverse. In such an input / output relationship, if a torque cam is provided between the output shaft 2 and the second disk 60, thrust can be generated by the input rotational power.

1 Input shaft (first power transmission shaft)
2 Output shaft (second power transmission shaft)
DESCRIPTION OF SYMBOLS 9 Casing 10 1st drive connection mechanism 11 Torque cam 12 Input part 13 Rolling body 14 Output part 15 1st bevel gear 16 2nd bevel gear 17 1st rotating shaft 17c Spline groove | channel 20 2nd drive connecting mechanism 21 3rd rotating shaft 22 2nd 3 bevel gears 23 4th bevel gear 24 2nd rotating shaft 24c spline shaft 30 1st roller 30a outer periphery 40 1st disk 40a 1st disk surface 40b 1st back surface 40c rotation center part 50 2nd roller 50a outer periphery 60 2nd disk 60a 1st disk 2 board 60b second rear 60c rotation center 70 housing member 70a a female threaded hole 80 actuator mechanism 81 motor 82 output shaft C ₁ main axis C _11, C _12, C ₁₃ input axis (a first orthogonal axis)
C ₂₁ , C ₂₂ , C ₂₃ output side axis (second orthogonal axis)

Claims (10)

A friction type continuously variable transmission interposed between a first power transmission shaft and a second power transmission shaft disposed coaxially on a main axis;
A first roller that is drivingly connected to the first power transmission shaft and supported by the first rotation shaft so as not to be relatively rotatable and axially movable;
A first disk disposed coaxially with the main axis and having a first disk surface in frictional contact with an outer periphery of the first roller to transmit rotational power to the first roller;
A second roller drivingly connected to the first disk and supported by the second rotating shaft so as not to be relatively rotatable and axially movable;
A second shaft that is disposed coaxially with the main axis, is drivingly connected to the second power transmission shaft, and has a second surface that frictionally contacts the outer periphery of the second roller, and transmits rotational power to the second roller. A friction type continuously variable transmission comprising: a disk. The first rotation axis is disposed coaxially with a first orthogonal axis orthogonal to the main axis,
The first roller is coupled to the first power transmission shaft via a first drive coupling mechanism,
The second rotation axis is disposed coaxially with a second orthogonal axis orthogonal to the main axis,
The friction type continuously variable transmission according to claim 1, wherein the second roller is connected to the first disk via a second drive connecting mechanism. A plurality of the first rotation shaft and the second rotation shaft are provided radially at equal intervals around the main axis,
The said 1st roller is equipped with each of the said some 1st rotating shaft, Each said 2nd rotating shaft is equipped with the said 2nd roller, The 1st or 2 characterized by the above-mentioned. Friction type continuously variable transmission. The first rotating shaft and the second rotating shaft are arranged in parallel with each other and are paired.
The first roller and the second roller are provided between the first disk and the second disk,
The first roller and the second roller supported respectively by the first rotation shaft and the second rotation shaft that are parallel to each other are rotatably supported, and the force in the direction along the main axis can be transmitted. The friction type continuously variable transmission according to any one of claims 1 to 3, wherein a housing member is provided. The housing member is provided to be movable along the first rotating shaft and the second rotating shaft,
5. The friction type continuously variable transmission according to claim 4, further comprising an actuator mechanism for moving the housing member along the first rotation shaft and the second rotation shaft. 6. The friction type continuously variable transmission according to claim 4, further comprising a torque cam that generates thrust in a direction in which the first disk and the second disk are brought close to each other. The first power transmission shaft is an input shaft to which rotational power is input,
The second power transmission shaft is an output shaft from which rotational power is output,
The friction type continuously variable transmission according to claim 6, wherein the torque cam generates the thrust in a direction in which the first disk approaches the second disk by rotational power input to the input shaft. . The friction type continuously variable transmission according to claim 7, further comprising a casing that supports the second disk so as to be capable of resisting a thrust by the torque cam and is relatively rotatable. The first drive coupling mechanism includes:
A first bevel gear disposed coaxially with the main axis and drivingly coupled to the first power transmission shaft;
The first rotating shaft;
A second bevel gear that is coaxially fixed to the first rotation shaft, meshes with the first bevel gear, and is arranged on the outer peripheral side of the first roller with respect to the main axis. The friction type continuously variable transmission according to any one of claims 3 to 8, wherein the friction type continuously variable transmission according to claim 2 or 2 is cited. The second drive coupling mechanism is
A third bevel gear that is disposed coaxially with the main axis and is fixed to a third rotating shaft that is coupled to the rotation center of the first disk;
The second rotating shaft;
A fourth bevel gear fixed on the same axis as the second rotation shaft and meshing with the third bevel gear, and disposed on the inner peripheral side of the second roller with respect to the main axis. The friction type continuously variable transmission according to any one of claims 3 to 9, wherein the friction type continuously variable transmission according to claim 2 or 2 is cited.

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