JPH11141631A - Variable diameter pulley - Google Patents

Abstract

PROBLEM TO BE SOLVED: To simplify a structure for speed change, simplify a structure for a belt transmission, if applied for the belt transmission, and reduce a manufacturing cost and an arrangement space. SOLUTION: A pair of pulley main bodies 2, 3 are arranged around a shaft 1 and a power transmission ring 6 to engage a belt 7 is held between mutually opposed power transmission planes 4, 5 of the pulley main bodies 2, 3. Both pulley main bodies 2, 3 are connected with a diaphragm spring 11 to be integrally rotatable and energized to directions of approaching each other. A wedge storage space 48 is provided between the back 28 of the pulley main body 3 and an opposite member 44 to store an inertial member 47 therein. As a rotating speed becomes faster, the inertial member 47 is displaced to the narrower storage space with centrifugal force and cooperated with the diaphragm spring 11 for both pulley main bodies 2, 3 to approach each other to automatically displace the power transmission ring 6 to the concentrical side.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable diameter pulley capable of changing an effective diameter of a belt.

[0002]

2. Description of the Related Art Heretofore, there has been provided a belt transmission device using a variable-diameter pulley capable of changing an effective diameter of a belt. In this belt transmission device, the belt pulls up while increasing the belt tension by a speed ratio adjusting tensioner driven by a driving means such as a hydraulic actuator or an electric motor. To change gears.

[0003]

However, this belt transmission uses a mechanism such as a tensioner for adjusting the speed ratio, a drive mechanism for driving the tensioner, and a controller for controlling the operation of the drive mechanism. Therefore, there are problems that the number of parts is large, the structure is complicated, the manufacturing cost is high, and the arrangement space is wide.

Accordingly, an object of the present invention is to simplify the structure for shifting and, when applied to a belt transmission, to simplify the structure of the belt transmission and to reduce the manufacturing cost and the space required for arrangement. To provide a variable diameter pulley that can be used.

[0005]

According to a first aspect of the present invention, there is provided a variable diameter pulley capable of changing an effective diameter with respect to a belt. First and second pulley bodies provided movably in the axial direction on the first and second tapered first and second power transmission surfaces respectively formed on opposing surfaces of the pulley bodies; A power transmission ring, which is eccentrically sandwiched by the power transmission surfaces with respect to the shaft centers of both pulleys and has a belt wound around the outer peripheral surface, is connected to the first pulley main body so as to be integrally movable in the axial direction. An opposing member including an opposing surface opposing the back surface of the power transmission surface of the second pulley main body;
An elastic member interposed between the rear surface of the second pulley main body and the elastic member interposed between the main body and the rear surface of the second pulley main body to urge the two pulley main bodies toward each other. An inertia member that is housed and displaces the housing space in the centrifugal direction to bias the power transmission ring to a position concentric with the axis through the two pulley bodies. .

In this configuration, the force for displacing the power transmission ring toward the eccentric side by the belt tension and the force for displacing the power transmission ring to the concentric side via the two pulleys mainly by the elastic member and the inertia member. The power transmission ring is displaced to a position where the power is balanced. Therefore, the centrifugal force of the inertia member increases with the rotation speed of both pulleys, and the force by which the elastic member and the inertia member try to displace the power transmission ring concentrically, the belt tension acts on the power transmission ring. If the force is larger than the force to be displaced to the eccentric side, the power transmission ring is displaced to the concentric position. Conversely, the centrifugal force of the inertia member decreases as the rotational speed of both pulleys decreases, and the force by which the elastic member and the inertia member try to displace the power transmission ring concentrically is the belt tension. Becomes smaller than the force for displacing the power transmission ring toward the eccentric side, the power transmission ring becomes eccentric.

Here, the accommodation space for accommodating the inertial member is
It is necessary to have a wedge shape in which the width in the axial direction becomes smaller as going outward in the radial direction. For that purpose, at least one of the back surface of the second pulley main body and the facing surface of the facing member may be formed in a tapered shape. According to a second aspect of the present invention, in the variable diameter pulley according to the first aspect, the inertial member includes a rolling member that rolls on an opposing surface of the opposing member and a back surface of the main body of the second pulley. Things.

In this configuration, the inertia member can be smoothly displaced by rolling the rolling member. It is possible to prevent a situation in which the inertial member is pinched between the opposing surface of the opposing member and the rear surface of the second pulley main body and does not move. Examples of the above-mentioned rolling member include a ball and a roller. In the case of a roller, it is preferable to provide a groove to guide the movement in the centrifugal and centripetal directions, and when the surface on which the roller rolls is a tapered surface, it is preferable to crown the outer peripheral surface of the roller.

Further, a shaft member that penetrates the rollers may be provided, and the shaft members may rotatably support the rollers via a bearing such as a metal bush. In this case, the rollers may be guided by one of the facing surface of the facing member and the back surface of the main body of the second pulley, and the shaft member may be guided by the other. The variable diameter pulley according to the third aspect of the present invention
3. The first connection means according to claim 1 or 2, wherein the first connection means connects the two pulley bodies so as to be integrally rotatable, and the second connection means connects the two pulley bodies to the rotation shaft via the first connection means. Means are further provided.

In this configuration, the second connecting means connects the two pulley bodies to the rotary shaft at a time through the first connecting means for connecting the two pulley bodies so as to be integrally rotatable. Compared to the case where the
The structure can be simplified. According to a fourth aspect of the present invention, in the variable diameter pulley according to the third aspect, the first connecting means includes a diaphragm spring whose inner diameter portion and outer diameter portion are integrally rotatably engaged with the corresponding pulley bodies. The diaphragm spring also serves as the elastic member.

In this configuration, since the diaphragm spring that connects the two pulleys so as to be integrally rotatable also serves as an elastic member, the structure can be simplified. Also,
Since the diaphragm spring can directly urge both pulley main bodies, the both pulley main bodies can be smoothly displaced, so that a smooth shift can be achieved. According to a fifth aspect of the present invention, in the variable diameter pulley according to the fourth aspect, the diaphragm spring includes a plurality of connection holes arranged at a radially intermediate portion at circumferentially spaced intervals. It is characterized by including a connection shaft engaged with the inner surface of the connection hole so as to restrict only the circumferential displacement of the diaphragm spring.

In this configuration, by setting the radial position of the connection hole of the diaphragm spring to a predetermined value, the inner diameter portion and the outer diameter portion of the diaphragm spring are mutually opposite (with respect to the axial position of the connection hole) and are equal to each other. Axial displacement can be performed by the displacement amount. As a result, both pulley bodies can be axially displaced in opposite directions by the same amount of displacement, so that the center of the belt can be kept constant.

According to a sixth aspect of the present invention, in the variable diameter pulley according to the third aspect, the first connecting means comprises a pair of first pulley main bodies and a pair of oppositely formed slopes respectively formed on the facing member. The pair of cam surfaces convert the relative rotation of the corresponding pulley main body with respect to the rotation axis into the axial displacement of the corresponding pulley main body, thereby connecting the two pulley main bodies to each other. It is characterized in that it is displaced in the axial direction with the same amount of displacement in the opposite direction.

In this configuration, for example, when a fluctuating load torque is applied, this load torque is converted into a force for bringing both pulley main bodies closer to each other by the pair of cam surfaces. The clamping force to be clamped can be increased. Thereby, it is possible to prevent the occurrence of slippage between the power transmission ring and the power transmission surface mainly composed of both pulleys.

According to a seventh aspect of the present invention, in the variable diameter pulley according to the sixth aspect, a pair of guide grooves for guiding a connecting shaft are formed in the first pulley main body and the opposing member, respectively. The cam surfaces are formed by the inner surfaces of the pair of guide grooves, respectively. In this configuration, since the cam surface is provided on the inner surface of the guide groove for guiding the connecting shaft, the rotational displacement of both pulleys can be smoothly converted to the axial displacement. It is preferable that the connecting shaft is provided with a rolling member that rolls on the inner surface of the guide groove, because smoother conversion is possible.

[0016]

Preferred embodiments of the present invention will be described below with reference to the accompanying drawings. FIG. 1 is a sectional view of a variable diameter pulley A according to one embodiment of the present invention. FIG.
FIGS. 3A and 3B are schematic configuration diagrams illustrating a main part of a belt-type continuously variable transmission system B using the variable diameter pulley A. FIG.

The variable-diameter pulley A is arranged with respect to the shaft center K as shown in FIG.
A power transmission ring 6 that can be displaced from an eccentric state as shown in FIG. 2A to a concentric state as shown in FIG.
And the effective diameter of the belt 7 wound around the power transmission ring 6 can be changed. The power transmission ring 6 is sandwiched between the first and second pulley bodies 2 and 3.

Although the variable diameter pulley A can be applied to at least one of a driving pulley and a driven pulley, this embodiment will be described based on an example applied to a driven pulley. In the present system B, the endless belt 7 is wound around the power transmission ring 6 of the variable-diameter pulley A via a displaceable tensioner pulley 56 of a tensioner 55 and a fixed idler pulley 58. The tensioner 55 is
The tensioner pulley 56 includes an elastic member 57 that urges the belt 7 in a direction in which the belt 7 approaches.
Attempts to eccentrically move the power transmission ring 6 through the belt 7.

On the other hand, the variable diameter pulley A is provided with a biasing member for biasing the power transmission ring 6 to the concentric position side via the pulley main bodies 2 and 3, as will be described in detail later. The biasing member is an elastic member (corresponding to the diaphragm spring 11 in FIG. 1) that generates a loose-side tension G on the belt 7 via the power transmission ring 6 in accordance with the relative displacement of the pulley bodies 2 and 3 in the axial direction. ), And an inertia member (corresponding to the inertia member 47 in FIG. 1) that generates the loose side tension H on the belt 7 via the power transmission ring 6 according to the rotation speed of the variable diameter pulley A.

A position where the resultant force (G + H) of the tensions G and H generated by the elastic member and the inertia member of the variable diameter pulley A and the tension F of the belt 7 generated by the elastic member 57 of the tensioner 55 are balanced. Then, the power transmission ring 6 and the elastic member 57 of the tensioner 55 are displaced. The inertia member is displaced in the centrifugal direction according to the rotation speed, and biases the power transmission ring 6 to the concentric position side via the pulley main bodies 2 and 3, and the centrifugal member that adjusts the gear ratio according to the rotation speed. It functions as an automatic speed ratio adjustment mechanism.

That is, when the running speed of the belt 7 is relatively low, the tension H due to the inertial member is small. Therefore, as shown in FIG. 2A, when the elastic member 57 of the tensioner 55 is displaced to the contraction side and the power transmission ring 6 is displaced to the eccentric side, the tension F and the tension G + H are balanced. become. Therefore, the effective diameter of the belt 7 becomes smaller with respect to the variable diameter pulley A, and the rotation speed of the rotating shaft provided with the variable diameter pulley A becomes relatively faster than the rotation speed of the driving pulley.

Conversely, when the running speed of the belt 7 is high, the tension H due to the inertia member is large. Therefore, FIG.
As shown in (b), in a state where the elastic member 57 of the tensioner 55 is displaced to the extension side and the power transmission ring 6 is displaced to the concentric side, the tension F and the tension G + H are balanced. Therefore, with respect to the variable diameter pulley A, the belt 7
Has a large effective diameter, and the rotation speed of the rotary shaft provided with the variable diameter pulley A is relatively slower than the rotation speed of the drive pulley.

FIG. 3 is a graph showing the relationship between the rotation speed of the driving pulley and the rotation speed of the variable-diameter pulley. In FIG. 3, power is transmitted in the region where the rotation speed of the driving pulley reaches the rotation speed V1. The ring 6 is eccentric with the maximum amount of eccentricity, and the rotation speed of the variable diameter pulley A increases at a constant increase rate. In the range from the rotation speed V1 to the rotation speed V2, the eccentricity of the power transmission ring 6 is gradually reduced to increase the effective diameter of the variable-diameter pulley A. Therefore, the rotation speed of the variable-diameter pulley A increases from the range. The ratio decreases. When the rotation speed V3 is reached, the power transmission ring 6 becomes concentric, and the variable diameter pulley A has the maximum effective diameter. In the region where the rotation speed is V3 or higher, the rotation speed of the variable diameter pulley A is increased at a slightly smaller rate than the region. Increase.

Referring to FIGS. 1 and 4, the variable diameter pulley A includes a rotating shaft 1 which is integrally rotatably connected to, for example, a rotating shaft of an auxiliary machine of an automobile. The two pulley bodies 2 and 3 are movable in the axial direction of the rotary shaft 1 and have an annular shape. These pulley main bodies 2 and 3
Are formed with conical tapered power transmission surfaces 4 and 5, respectively. These pair of power transmission surfaces 4,
5 are tapered so as to be inclined in opposite directions to each other.
Are held eccentrically with respect to the axis K of the pulley main bodies 2 and 3. The power transmission ring 6 has a substantially trapezoidal cross section. FIG. 1 shows a state where the power transmission ring 6 is eccentric with the maximum amount of eccentricity, and FIG. 4 shows a state where the power transmission ring 6 is at the concentric position. The effective diameter D of the belt 7 is changed according to the displacement of the power transmission ring 6. L is a position of the width center of the belt 7 (hereinafter, referred to as a belt center L).

A power transmission surface 8 to the belt 7 is formed on the outer peripheral surface of the power transmission ring 6, and the belt 7 is wound around the power transmission surface 8. The transmission surface 8 has a rib 7a of the belt 7
A peripheral groove 8a is formed which meshes with. Both side surfaces of the power transmission ring 6 constitute power transmission surfaces 9 and 10 that contact the corresponding power transmission surfaces 4 and 5 to transmit torque.

The belt 7 is preferably made of rubber. As the power transmission ring 6, carbon fiber, aromatic polyamide fiber and graphite are mixed with a resin having excellent durability and a high friction coefficient, for example, phenol resin. It is preferable to use a molded resin material. With this resin, despite its high strength and excellent wear resistance,
The aggressiveness to the mating member is gentle, and the friction coefficient is stable regardless of the temperature. The content ratio of carbon fiber, aromatic polyamide fiber and graphite in the resin material is 5 to 30% by weight of carbon fiber, 5 to 15% by weight of aromatic polyamide fiber, and 10 to 10% by weight of graphite.
Being in the range of 15% by weight improves wear resistance,
This is preferable in that the coefficient of friction is made more stable.

The variable diameter pulley serves as an urging means for urging the first and second pulley main bodies 2 and 3 in a direction approaching each other, and connects the two pulley main bodies 2 and 3 so as to be integrally rotatable. 1 is provided with a diaphragm spring 11 as a connecting means.
Is connected via a plurality of connection shafts 13 to a connection portion 12 formed of a conical annular plate that rotates in conjunction with the rotation shaft 1 so as to be integrally rotatable. A second connecting means is constituted by the connecting portion 12 and the plurality of connecting shafts 13. An inner peripheral portion of the connecting portion 12 is connected to an outer peripheral portion of a flange portion la formed integrally with the rotating shaft 1 so as to be integrally rotatable by a spline connection. Movement has been stopped.

The inner diameter portion 14 and the outer diameter portion 15 of the diaphragm spring 11 are respectively engaged with the first and second pulley bodies 3 so as to be integrally rotatable. Thereby, both pulley main bodies 2 and 3 and diaphragm spring 1
1 is configured to rotate integrally with the rotating shaft 1. For example, when this variable diameter pulley is applied to a driven pulley as in the present embodiment, the power transmission ring 6,
Torque is transmitted to the rotating shaft of the accessory via the two pulley main bodies 2 and 3, the diaphragm spring 11 and the rotating shaft 1.

Referring to FIG. 1 and FIG. 5, radial connection grooves 16 and 17 which are respectively arranged on the inner diameter part 14 and the outer diameter part 15 of the diaphragm spring 11 are arranged at equal circumferences.
Are formed. In addition, the diaphragm spring 11
In the radially intermediate portion, connecting holes 31 that penetrate the above-described connecting shaft 13 and connect the diaphragm spring 11 and the connecting portion 12 so as to be able to transmit torque are formed in a circle at equal intervals.

Referring to FIG. 1, first pulley main body 2 includes
A disk portion 18 having the power transmission surface 4 formed thereon, and a shaft portion 19 fixed to the inner periphery of the disk portion 18 so as to be integrally rotatable and arranged concentrically with the rotating shaft 1 are provided. This shaft 19
A tapered portion 20 is formed at one end of the tapered portion.
The disk portion 18 is fitted into the base plate and fixed by a nut 21.

The other end of the shaft portion 19 has a cylindrical boss portion 2 concentric with the rotating shaft 1 and having a diameter larger than that of the shaft portion 19.
2 are integrally formed. The boss portion 22 is slidably supported in the axial direction on the peripheral surface of the rotating shaft 1 via a bush 23 as a sliding bearing. The second pulley main body 3 includes a conical disk portion 24 forming the power transmission surface 5.
And a cylindrical boss portion 25 formed on the inner periphery of the disk portion 24. Boss portion 25 of second pulley main body 3
Surrounds a portion of the shaft portion 19 of the first pulley main body 2 and a part of the boss portion 22, and the shaft portion 19 of the first pulley main body 2
And bosses 22 are slidably supported in the axial direction via bushes 26 and 27 as sliding bearings, respectively.

The back surface 28 of the power transmission surface 5 of the second pulley main body 3 is formed as a conical tapered surface having a generatrix parallel to the power transmission surface 5. The outer peripheral edge of the second pulley main body 3 has a section L
A ring-shaped annular flange portion 32 is integrally extended, and a plurality of connecting grooves 17 of the outer diameter portion 15 of the diaphragm spring 11 are fitted into a surface of the annular flange portion 32 on the side of the diaphragm spring 11. A plurality of plate-like connecting projections 29 are formed radially at equal intervals on the circumference. The annular flange portion 32 of the second pulley main body 3 is pressed by the outer diameter portion 15 of the diaphragm spring 11 so that the second pulley main body 3 approaches the first pulley main body 2 (to the left in FIG. 1). Being energized.

The shaft 19 and the boss 22 of the first pulley main body 2 extend through the boss 25 of the second pulley main body 3 toward the back surface 28 of the power transmission surface 5 of the second pulley main body 3. The boss portion 22 constitutes a portion extending to the back side of the second pulley main body 3. At the end of the boss portion 22 as a portion extending to the rear side, a connecting portion 30 formed of an annular flange for integrally rotating the end portion and the inner diameter portion 14 of the diaphragm spring 11 is integrally formed. ing.

The inner peripheral portion of the connecting portion 30 is screwed to the end of the boss portion 22 and is fixed so as to be integrally rotatable. The torque transmitted via the connecting portion 30 acts in the screw tightening direction, so that the fixing is not loosened. The connecting portion 30 has a pressing surface 33 for pressing the inner diameter portion 14 of the diaphragm spring 11 in the axial direction,
A plurality of connecting projections 34 are formed on the pressing surface 33 and are radially formed at equal circumferential intervals. The above-mentioned pressing surface 33 is pressed by the inner diameter portion 14 of the diaphragm spring 11, and the first pulley main body 2 approaches the second pulley main body 3 via the connecting portion 30, the boss portion 22, and the shaft portion 19 (FIG. 1 (to the right). The plurality of connection protrusions 34 are fitted into the plurality of connection grooves 16 of the inner diameter portion 14 of the diaphragm spring 11, respectively.

The connecting portion 12 has a plurality of through-holes 35 that penetrate in the axial direction and are formed at equal intervals around the circumference.
5, the connection shaft 13 penetrating the washer member 40 and the connection hole 31 of the diaphragm spring 11 is inserted and fixed. That is, the diaphragm spring 1
Reference numeral 1 denotes a state in which the washer member 40 and the connecting portion 12 are sandwiched between the washer member 40 and the connecting portion 12 in the peripheral portion of the connecting hole 31. In order to allow the inclination at the time of displacement, the connecting shaft 13
Are formed on the inclined surfaces 41 and 42 having a conical taper shape centered at. Each connecting shaft 13 is formed in parallel with the axial direction of the rotating shaft 1 and is fitted into a connecting hole 31 of the diaphragm spring 11 so that the diaphragm spring 11
And the connecting portion 12 are connected so that torque can be transmitted. Connecting shaft 1
As 3, for example, a rivet with a head can be used, and when a rivet is used, it can be easily fixed by caulking the tip and expanding the diameter.

Referring to FIG. 6, connecting hole 31 is formed of a long hole extending in the radial direction. As shown in FIG. 6, a pair of parallel engaging surfaces 36 extending in the radial direction is formed on the inner surface thereof. , 3
7 are formed. On the other hand, the connecting shaft 13 has a so-called two-sided cross-sectional shape, and a pair of engaging surfaces 3 respectively engaging with a pair of engaging surfaces 36 and 37 of the connecting hole 31.
8,39.

The pair of engagement surfaces 36 and 37 of the connection hole 31
Than the pair of engagement surfaces 38 and 39 of the corresponding connection shaft 13,
It is set to be longer in the radial direction of the diaphragm spring 11. Each of the engagement surfaces 36 to 39 is a surface parallel to the axial direction (the direction perpendicular to the paper surface in FIG. 6) and the radial direction (the vertical direction in FIG. 6) of the diaphragm spring 11. Both engagement surfaces 36 and 37 of the connection hole 31
The width between them is set substantially equal to the width between both engagement surfaces 38 and 39 of the connection shaft 13. Thus, the connection shaft 1
3 is engaged with the inner surface of the connection hole 31 so as to restrict only the displacement of the diaphragm spring 11 in the circumferential direction R.

The radial position of the connecting hole 31 (FIGS. 1 and 4)
At the distance d from the axis K) is temporarily
3 restricts the axial displacement of the diaphragm spring 11 at the position of the connection hole 31,
And the outer diameter portion 15 can be displaced in opposite directions by the same stroke amount. Referring again to FIGS. 1 and 4, boss portion 22 of first pulley main body 2
An opposing member 44 having an opposing surface 43 opposing the back surface 28 of the second pulley main body 3 is fixed to the outer periphery of the main body so as to be integrally rotatable. The opposing member 44 includes a disk portion 45 and a boss portion 4.
6 and the boss portion 46 is fitted on the outer periphery of the boss portion 22 of the first pulley main body 2.

An annular accommodation space 48 for accommodating an inertia member 47 is defined between the back surface 28 of the second pulley main body 3 and the opposing surface 43 of the opposing member 44 facing the second pulley main body 3.
The outside of the housing space 48 is defined by the annular flange portion 32 having an L-shaped cross section of the second pulley main body 3, and the inside of the housing space 48 is defined by the boss 25 of the second pulley main body 3. It is partitioned. Since the back surface 28 of the second pulley main body 3 is tapered, the accommodation space 48 has a wedge-shaped cross section in which the width becomes narrower outward in the radial direction.

The inertia member 47 is displaced in the accommodating space 48 in the centrifugal direction (from the state shown in FIG. 1 to the state shown in FIG. 4), and cooperates with the diaphragm spring 11 to form the two pulley main bodies 2. The power transmission ring 6 is urged to a position concentric with the axis K via the power transmission ring 3. 1 and 4
Referring to FIG. 7, inertia member 47 includes a roller 49 formed of a cylinder as a rolling member, and a spindle member 50 that penetrates through roller 49 in the axial direction. Further, the inertia member 47 includes a bearing 51 made of, for example, a metal bush that is interposed between the spindle member 50 and 49 to allow relative rotation between the roller 49 and the spindle member 50.

On the opposing surface 43 of the opposing member 44, both ends of the support shaft member 50 are supported at the edges 53 and 54 thereof.
A guide groove 52 for guiding the rolling movement of the roller 49 is formed in the radial direction. The outer circumferential surface of the roller 49 may be crowned along the axial direction. Inertia member 47
Generates a centrifugal force that increases with the rotation speed. When the inertia member 47 increases the turning diameter by this centrifugal force and moves toward the narrow side (radially outward) of the housing space 48, the two pulley main bodies 2 and 3 approach each other, and the power transmission ring 6 moves to the concentric position side. Will be displaced.

In this embodiment, the built-in inertia member 47
With a simple structure using the centrifugal force, the effective diameter D of the variable-diameter pulley A can be automatically changed, and the speed can be changed automatically. As a result, in a belt-type continuously variable transmission system using the variable diameter pulley A, a tensioner for adjusting a gear ratio,
It is not necessary to use a drive mechanism for driving the tensioner and a mechanism such as a controller for controlling the operation of the drive mechanism, and a general passive tensioner 55 is used.
It is sufficient to use a so-called auto-tensioner, so that the structure can be significantly simplified, and the manufacturing cost and arrangement space can be reduced.

In addition, the inertia member 47 rolls on the back surface 28 of the second pulley main body 3 that partitions the accommodation space 48.
As a result, the inertial member 47 can be displaced smoothly, and as a result, it is possible to prevent the inertial member 47 from being stuck in the housing space 48 and not moving. Further, the connecting portion 12 as a second connecting means
However, since both pulley main bodies 2 and 3 are collectively connected to rotary shaft 1 via diaphragm spring 11 as first connecting means, each pulley main body 2 and 3 is individually connected to rotary shaft 1. In comparison, the structure can be simplified.

Further, since the diaphragm spring 11 for connecting the two pulley bodies 2 and 3 so as to be integrally rotatable also serves as an urging member, the structure can be simplified. Further, since the diaphragm spring 11 can directly bias the pulley main bodies 2 and 3, the both pulley main bodies 2 and 3 can be smoothly displaced, so that a smooth shift can be performed. Further, the inner diameter portion 14 and the outer diameter portion 1 of the diaphragm spring 11
Since the two pulley bodies 2 and 3 connected to 5 can be axially displaced symmetrically with the same displacement amount, the belt center L is maintained constant while smooth shifting is achieved with a simple structure. Can be.

The diaphragm spring 11 bends in accordance with the displacement of the two pulley bodies 2 and 3. Even if the axial displacement differs between the inner diameter portion 14 and the outer diameter portion 15, the connecting shaft 13 is moved by the diaphragm spring 11. Since the axial displacement of the portion of the connection hole 31 is allowed, no excessive stress is generated around the connection hole 13. As a result, the durability of the diaphragm spring 11 can be improved. Further, since the center of the power transmission ring always coincides with the position of the belt center, no vibration or abnormal wear occurs on the power transmission ring.

In particular, in the present embodiment, the connecting shaft 13 has a pair of engaging surfaces 36 and 37 long along the radial direction of the connecting hole 31.
Therefore, a large contact area can be ensured, and the stress applied to the diaphragm spring 11 can be further reduced. As a result, the durability can be further improved. Further, the pulley bodies 2 and 3 follow the displacement of the belt 7 in the width direction and are displaced to a position corresponding to the actual belt center L, so that a smooth shift can be achieved with a simple structure.

If the width across flats of the connecting shaft 13 is ensured to secure the above-mentioned contact area, the bending rigidity of the connecting shaft 13 will be increased secondarily, and as a result, the connecting shaft 13 at the time of torque load will be increased. As a result, it is possible to prevent the diaphragm spring 11 and its connection hole 31 from being adversely affected. In the above embodiment, the connection hole 3 of the diaphragm spring 11
The axial displacement around 1 may be restricted by the connecting shaft 13. In this case, a universal joint may be interposed between the connection shaft 13 and the connection hole 31.

FIG. 8 shows a variable diameter pulley according to another embodiment of the present invention. Referring to FIG. 8, this variable diameter pulley A1 mainly differs from the variable diameter pulley of FIG. 4 in the following 1) to 3). 1) In the embodiment shown in FIG. 4, the first connecting means for connecting the two pulley bodies 2 and 3 so as to be integrally rotatable is constituted by the diaphragm spring 11.
1, the two pulley bodies 2 and 3 also serve as elastic members for urging in a direction approaching each other. In the present embodiment, however, the first connecting means is formed by an opposing member fixed to the first pulley body 62. The elastic member is formed by a compression coil spring 85 interposed between the second pulley main body 62 and the opposing member 69 while the member 69 is constituted by a plurality of connecting shafts 89 and 90 for connecting the second pulley main body 62 to the second pulley main body 62. Configured.

2) In the embodiment shown in FIG. 4, the position of the connecting hole 31 of the diaphragm spring 11 in the radial direction is set as required so that the two pulley bodies 2 and 3 are displaced in the axial direction symmetrically to each other. In the present embodiment, the rollers 97, 97 provided at both ends of the connecting shaft 90 included in the first connecting means are connected to the first pulley main body 62.
And cam surfaces 10 formed on the opposing member 69, respectively.
Achieved by engaging 0, 101 respectively.
Each cam surface 100, 101 and the corresponding cam surface 100, 1
A pair of conversion mechanisms T, T (), which convert the rotational angular displacement of each of the pulley main bodies 62, 63 with respect to the rotary shaft 61 into axial displacements in opposite directions to each other, by rollers 97, 97 as cam followers respectively engaged with the cam shaft 01. (Also referred to as a torque cam mechanism).

3) In the present embodiment, the inertia member and the rolling member are constituted by the balls 82. More specifically, referring to FIG. 8, the variable diameter pulley A1 includes first and second annular pulley main bodies 62 and 63 that are rotatable around a rotation shaft 61 and movable in the axial direction. Equipped,
Power transmission surfaces 64 and 65 are formed on the opposing surfaces of the pulley bodies 62 and 63, respectively. The pair of power transmission surfaces 64 and 65 are tapered so as to be inclined in opposite directions, and the power transmission ring 6 having a substantially trapezoidal cross section is formed by the two power transmission surfaces 64 and 65.
63 are eccentrically held with respect to the axis K. FIG. 8 shows a state in which the power transmission ring 6 is concentric with the axis K.

The first pulley main body 62 includes a conical disk portion 66 and a cylindrical boss portion 67 formed on the inner periphery of the disk portion 66. The disk portion 66 forms the power transmission surface 64 described above. Further, the boss portion 67 is provided with
Are slidably supported in the axial direction on bushings 68, 68 as sliding bearings. An end of the boss portion 67 is integrally connected to a later-described opposing member 69 by a screw 70. Reference numeral 71 denotes the first pulley main body 62 having the rotating shaft 6.
The stopper 71 is a stopper for preventing the shaft 1 from being pulled out. The stopper 71 is fixed to the rotating shaft 61 by a nut 72 screwed into an end of the rotating shaft 61.

The second pulley main body 63 includes an annular plate portion 73 having a circular plate extending around the outer periphery of a conical plate with holes, and an inner cylindrical portion extending around the inner periphery of the annular plate portion 73. Boss part 74
And an outer cylindrical portion 75 extending around the outer periphery of the annular plate portion 73, and an intermediate cylindrical portion 76 formed at a radially intermediate portion of the annular plate portion 73. The boss 74, the outer cylinder 75, and the intermediate cylinder 76 all have a power transmission surface 65 of the second pulley main body 63.
Is formed so as to extend to the back surface 77 side of. The boss portion 74 of the second pulley main body 63 is supported on the outer peripheral surface of the boss portion 67 of the first pulley main body 62 movably in the axial direction via a bush 78 as a sliding bearing.

The opposing member 69 is formed of an annular member, and the tapered portion 7 on the back surface 77 of the second pulley main body 63.
9 has a tapered opposing surface 80. Then, the boss 74 of the second pulley main body 63 and the intermediate cylindrical portion 76
A housing space 81 is formed by the tapered portion 79 of the back surface 77 and the facing surface 80 of the facing member 69, and a plurality of balls as an inertia member and a rolling member are formed in the housing space 81. 82 are accommodated. The accommodating space 81 has a wedge-shaped cross section in which the width becomes narrower outward in the radial direction.
Is displaced in the centrifugal direction, so that both pulley main bodies 2, 3
Can be brought closer to each other.

The opposing member 69 has an inner cylindrical portion 83 radially inward of the opposing surface 80, and the annular end surface portion 84 of the inner cylindrical portion 83 is 1
Is fixed to the end of the boss portion 67 of the pulley main body 2.
Thereby, the opposing member 69 rotates integrally with the first pulley main body 62 and moves integrally with the first pulley main body 62 in the axial direction.

A compression coil spring 85 is housed in the inner cylindrical portion 83 of the opposing member 69 as an elastic member for urging the pulley main bodies 62 and 63 toward each other. One end (the left end in the figure) of the compression coil spring 85 is engaged with the stepped portion 87 of the boss 74 while being fitted to the small diameter portion 86 at the tip of the boss 74 of the second pulley main body 63. The second pulley main body 63 is pressed and urged toward the first pulley main body 62 through the stepped portion 87. On the other hand, the other end (the right end in the figure) of the compression coil spring 85 is
9 is engaged with the end surface portion 84 of the inner cylindrical portion 83 of the
The first pulley main body 62 is pressed and urged toward the second pulley main body 63 through the fourth pulley 4. Also, the compression coil spring 85
The inner cylindrical portion 83 of the facing member 69 and the second pulley main body 6
Since the expansion and contraction are guided by the small diameter portion 86 of the third boss portion 74, the displacement can be performed smoothly.

The outer peripheral portion 88 of the opposing member 69 and the outer cylindrical portion 75 of the second pulley main body 63 are connected to a plurality of connecting shafts 89, 9 arranged in the radial direction as first connecting means.
0, it is integrally rotatably connected. Connecting shaft 8
Reference numeral 9 has one end fixed to the outer peripheral portion 88 of the facing member 69 and the other end rotatably supporting a roller 92 via a bush 91 (see FIG. 9). The roller 92 is rotatably fitted and engaged in a guide groove 93 formed in the outer cylindrical portion 75 of the second pulley main body 63 and parallel to the rotating shaft 61 and having one end opened.

On the other hand, the intermediate portion of the connecting shaft 90 is
The outer cylindrical part 95 of the connecting part 94 as a second connecting means, which is formed in a two-stage cylindrical shape integrally formed around the outer periphery of the outer peripheral part, is fixed in a radial direction. 8 and 10 (a) and 10 (b), bush 9 is provided at both ends of connecting shaft 90, respectively.
6, a roller 97 is rotatably supported. Each of the rollers 97 includes a guide groove 98 formed in the outer cylindrical portion 75 of the second pulley main body 63 and an outer cylindrical portion 95 of the facing member 69.
Are rotatably fitted into and engaged with the guide grooves 99 formed in the guide grooves 99.

These guide grooves 98 and 99 are provided in FIG.
As shown in (a) and (b), they are inclined in opposite directions to each other, and cam surfaces 100 and 101 are formed by the inner surfaces of the guide grooves 98 and 99, respectively. When the two pulley bodies 62 and 63 generate a rotational angular displacement with respect to the rotation shaft 61 in accordance with the load torque on the variable diameter pulley A1, the cam surfaces 100 and 101 apply the rotational angular displacement to the two pulley bodies 62. , 63, and is converted into the axial displacement of FIG.
As shown in (b), both pulley bodies 62 and 63 are axially displaced in opposite directions and with the same amount of displacement (so-called torque cam mechanism). As a result, the position of the belt center L is maintained constant irrespective of the shift. FIG. 9A shows the power transmission ring 6.
Corresponds to the state shown in FIG.
Corresponds to a state where the power transmission ring 6 is eccentric.

In this embodiment, the same components as those in the embodiment of FIG.
The description is omitted. According to the present embodiment, similarly to the embodiment of FIG. 1, the resultant force (G + H) of the tension applied to the belt 7 by the compression coil spring 85 as the elastic member and the ball 82 as the inertial member, The power transmission ring 6 is automatically displaced to a position where the tension F applied to the belt 7 by the elastic member 57 is balanced, and has a simple structure utilizing the centrifugal force of the inertial member composed of the built-in ball 82. Thus, the automatic transmission can be achieved by automatically changing the effective diameter D of the variable diameter pulley A1.

Further, since the ball 82 serving also as a rolling member is used as the inertia member, the structure can be further simplified, and the occurrence of a situation in which the inertia member is pinched in the housing space 81 and does not move can occur. It can be prevented before it happens.
Further, when the load torque is applied, the two pulley main bodies 62 and 63 are brought close to each other by the function of the cam surfaces 100 and 101 included in the conversion mechanism (torque cam mechanism) T, and the force for clamping the power transmission ring 6 can be increased. Therefore, the power transmission ring 6 and the power transmission surfaces 64,
65 can be prevented from occurring. As a result, highly efficient power transmission becomes possible.

Further, since the cam surfaces 100 and 101 are provided on the inner surfaces of the guide grooves 98 and 99 to roll the rollers 97 and 97 at both ends of the connecting shaft 90, the two pulley main bodies 62 and 63 are formed. The relative rotation with respect to the rotation shaft 61 can be smoothly converted to the axial displacement. as a result,
Shifting can be performed smoothly. Further, the pulley main bodies 62 and 63 can be displaced symmetrically in the axial direction by the function of the cam surfaces 100 and 101, so that the belt center L can be kept constant regardless of the gear shift.

The present invention is not limited to the above embodiments, and various changes can be made within the scope of the present invention. For example, as the above-mentioned pair of conversion mechanisms T included in the variable-diameter pulley, a pair of screw coupling mechanisms having mutually opposite screws can be used. Further, when the present invention is applied to a belt transmission, it is not limited to using a general passive type tensioner (a so-called auto tensioner) as a tensioner, and the operating position of a tensioner pulley is actively changed. It is of course possible to use a tensioner for adjusting the speed ratio.

[0063]

According to the first aspect of the present invention, the power transmission ring is automatically displaced concentrically or eccentrically by a simple structure using the centrifugal force of the built-in inertia member, and the speed is automatically shifted. Can be. As a result, in a belt transmission using the variable diameter pulley, a tensioner for speed ratio adjustment,
It is not necessary to use a driving mechanism for driving the tensioner and a mechanism such as a controller for controlling the operation of the driving mechanism, and it is sufficient to use a general passive type tensioner (so-called auto tensioner). Can be greatly simplified, and the manufacturing cost and arrangement space can be reduced.

According to the second aspect of the present invention, the inertia member can be smoothly displaced by using the rolling member.
It is possible to prevent a situation in which the inertia member is pinched in the housing space and does not move. According to the third aspect of the present invention, since the second connecting means connects both the pulley main bodies to the rotary shaft collectively, the structure is simplified as compared with a case where each pulley main body is individually connected to the rotary shaft. be able to.

According to the fourth aspect of the present invention, the diaphragm spring connecting the two pulleys so as to be integrally rotatable also serves as an urging member, so that the structure can be simplified. In addition, since the diaphragm spring can directly urge both pulley main bodies, the both pulley main bodies can be smoothly displaced, so that a smooth shift can be achieved. According to the fifth aspect of the present invention, the two pulley bodies connected to the inner diameter portion and the outer diameter portion of the diaphragm spring can be symmetrically displaced in the axial direction with the same amount of displacement. And the center of the belt can be maintained constant.

According to the present invention, when the load torque is applied, the force for clamping the power transmission ring can be increased by the two pulleys, so that the power transmission ring and the power transmission surface of both the pulleys can be increased. Slip can be prevented from occurring. According to the seventh aspect of the present invention, since the cam surface is provided on the inner surface of the guide groove for guiding the connecting shaft, the relative rotation of the two pulleys with respect to the rotating shaft can be smoothly converted to the axial displacement.

[Brief description of the drawings]

FIG. 1 is a sectional view of a variable diameter pulley according to an embodiment of the present invention, showing a state where a power transmission ring is eccentric.

FIG. 2 is a schematic view of a main part of a belt-type continuously variable transmission in which the variable diameter pulley of FIG. 1 is applied to a driven pulley.

FIG. 3 is a graph showing a relationship between rotation speeds of a driving pulley and a variable diameter pulley of FIG. 1;

FIG. 4 is a sectional view showing a state in which a power transmission ring is concentric in the variable diameter pulley of FIG. 1;

FIG. 5 is a front view of a diaphragm spring of the variable diameter pulley of FIG. 1;

FIG. 6 is a schematic view showing a combined state of a connection hole and a connection shaft of a diaphragm spring of the variable diameter pulley of FIG. 1;

FIG. 7 is a partially cutaway perspective view showing a main part of an opposing member fixed to a main body of a second pulley in the variable diameter pulley of FIG.

FIG. 8 is a sectional view of a variable diameter pulley according to another embodiment of the present invention, showing a state where a power transmission ring is at a concentric position.

9 is a side view showing a part of an outer peripheral surface of a main body of a second pulley in the variable diameter pulley of FIG. 8;

FIG. 10 is a schematic view showing a second pulley main body, an opposing member, and a connecting shaft with a roller for connecting these members in the variable diameter pulley shown in FIG. 8, wherein (a) shows a state in which a power transmission ring is located at a concentric position; (B) corresponds to a state where the power transmission ring is eccentric.

[Explanation of symbols]

A Variable Diameter Pulley 1 Rotary Shaft 2 First Pulley Main Body 3 Second Pulley Main Body 4,5 Power Transmission Surface 6 Power Transmission Ring 7 Belt 11 Diaphragm Spring (First Connection Means, Elastic Member) 12 Connection Section (Second Section) 13 Connecting shaft (second connecting means) 14 Inner diameter portion 15 Outer diameter portion 28 Back surface 31 Connecting hole 36, 37, 38, 39 Engaging surface 43 Opposing surface 44 Opposing member 47 Inertial member 48 Housing space 49 Roller (Rolling member) 50 Support shaft member 51 Bearing 52 Guide groove 55 Tensioner 56 Tensioner pulley 57 Elastic member 61 Rotary shaft 62 First pulley main body 63 Second pulley main body 64, 65 Power transmission surface 69 Opposing member 77 Back surface 80 Opposition Surface 81 Housing space 82 Ball (inertia member, rolling member) 85 Compression coil spring (elastic member) 89, 90 Connection shaft (first connection Means) 94 Connecting part (second connecting means) 96 Bush 97 Roller 98, 99 Guide groove 100, 101 Cam surface T conversion mechanism (torque cam mechanism)

Claims (7)

[Claims] 1. A variable diameter pulley capable of changing an effective diameter with respect to a belt, comprising: first and second annular pulley bodies provided movably in an axial direction of a rotating shaft; First and second tapered power transmission surfaces respectively formed on opposing surfaces; and a power transmission surface between which the belt is wound eccentrically with respect to the shaft center of both pulleys, and a belt is wound around the outer peripheral surface. A power transmission ring, an opposing member coupled to the first pulley main body so as to be integrally movable in the axial direction, and including an opposing surface facing the back surface of the power transmission surface of the second pulley main body; An elastic member interposed between the second pulley main body and the back surface of the second pulley main body; and an elastic member interposed between the second pulley main body and the rear surface of the second pulley main body. Collected in It is a variable diameter pulley wherein the by displacing the housing space in the centrifugal direction, the power transmission ring through the pulleys mainly equipped with an inertia member for biasing the axis concentric position. 2. The variable diameter pulley according to claim 1, wherein said inertia member includes a rolling member which rolls on an opposing surface of said opposing member and a back surface of a second pulley main body. 3. A first connecting means for connecting both pulley main bodies so as to be integrally rotatable, and a second connecting means for connecting both pulley main bodies to a rotating shaft via the first connecting means so as to transmit power. The variable diameter pulley according to claim 1 or 2, further comprising: 4. The first connecting means includes a diaphragm spring whose inner diameter portion and outer diameter portion are integrally rotatably engaged with corresponding pulley bodies, and the diaphragm spring also serves as the elastic member. The variable diameter pulley according to claim 3, wherein 5. The diaphragm spring includes a plurality of connection holes arranged at a radially intermediate portion at circumferentially spaced intervals, and the second connection means restricts only the circumferential displacement of the diaphragm spring. The variable diameter pulley according to claim 4, further comprising a connection shaft engaged with an inner surface of the connection hole. 6. The first connecting means includes a connecting shaft that engages with a pair of cam surfaces formed on the first pulley main body and the opposing member and having mutually opposite inclinations. The cam surface converts the relative rotation of the corresponding pulley main body with respect to the rotation shaft into the axial displacement of the corresponding pulley main body, thereby displacing the two pulley main bodies in the opposite directions in the axial direction with the same amount of displacement. The variable diameter pulley according to claim 3, wherein: 7. A pair of guide grooves for guiding a connecting shaft are formed in the first pulley main body and the opposed member, respectively, and the pair of cam surfaces are formed by inner surfaces of the pair of guide grooves, respectively. 7. The variable diameter pulley according to claim 6, wherein: