JP2018105429A - Belt continuous variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To avoid a deterioration in transfer efficiency due to slip loss of a belt without narrowing a shift range in a belt continuous variable transmission for performing continuous variable speed by changing each of pulley diameters of a primary pulley and a secondary pulley in transferring the rotation of the primary pulley connected to a power source to the secondary pulley connected to a drive part through the belt.SOLUTION: An auxiliary pulley 30 having a variable pulley diameter is interposed between a primary pulley 10 and a secondary pulley 20, transfer belts 41, 42 are wound around between the primary pulley 10 and the auxiliary pulley 30, and between the auxiliary pulley 30 and the secondary pulley 20, respectively, and the rotation of the primary pulley 10 is transferred to the secondary pulley 20 through the transfer belts 41, 42 step by step.SELECTED DRAWING: Figure 1

Description

  The present invention eliminates the need to change the pulley diameters of the primary pulley and the secondary pulley when transmitting the rotation of the primary pulley connected to the power source to the secondary pulley connected to the drive unit via the belt. The present invention relates to a belt-type continuously variable transmission that performs step shifting.

  Conventionally, primary pulleys and secondary pulleys with variable pulley diameters are used, the primary pulley is connected to the power source, the secondary pulley is connected to the drive unit, and an endless belt is wound around the primary pulley and the secondary pulley. Thus, the power generated by the power source is transmitted to the drive unit via the belt. In that case, continuously variable transmission is implement | achieved by changing the pulley diameter of a primary pulley and a secondary pulley, respectively (for example, refer patent document 1).

JP-A-2015-172426

  However, as described above, in the case of realizing continuously variable transmission by changing the pulley diameters of the primary pulley and the secondary pulley, when the rotation of the drive unit is low speed or high speed, either the primary pulley or the secondary pulley is used. By reducing the pulley diameter of one of the pulleys, the pulley contact area of the pulley with a reduced pulley diameter is reduced, which causes transmission loss due to slip loss and the output of a power source such as a vehicle engine. May not be transmitted effectively. If the pulley diameter is increased, slip loss is less likely to occur, but in that case, there arises a problem that the speed change range is narrowed.

  The present invention has been made in view of the problems of the conventional techniques as described above, and the rotation of the primary pulley connected to the power source is transmitted to the secondary pulley connected to the drive unit via the belt. In a belt-type continuously variable transmission that performs continuously variable transmission by changing the pulley diameters of the primary pulley and secondary pulley when transmitting, avoiding a decrease in transmission efficiency due to belt slip loss without narrowing the shift range It is an object of the present invention to provide a belt type continuously variable transmission that can be used.

In order to achieve the above object, the present invention provides:
A primary pulley connected to a power source and having a variable pulley diameter;
A secondary pulley that is coupled to a drive unit that is rotationally driven by power generated by the power source, and the pulley diameter is variable;
And at least one auxiliary pulley having a variable pulley diameter is arranged such that its rotation axes are parallel to each other,
Belts are respectively wound between the primary pulley and the auxiliary pulley, and between the auxiliary pulley and the secondary pulley, and when there are a plurality of the auxiliary pulleys, the belt is also interposed between the plurality of auxiliary pulleys. And the rotation of the primary pulley is transmitted to the secondary pulley via the belt.

Further, a primary pulley that is connected to a power source and includes a sheave pair that changes a pulley diameter by changing a distance between each other,
A secondary pulley that is connected to a drive unit that is rotationally driven by power generated by the power source, and includes a sheave pair that changes a pulley diameter by changing a mutual distance;
An auxiliary pulley including an input side sheave pair and an output side sheave pair that change the pulley diameter by changing the distance between them is arranged so that the rotation axes thereof are parallel to each other,
A first belt wound between sheaves constituting the sheave pair of the primary pulley and between sheaves constituting the input-side sheave pair of the auxiliary pulley;
A second belt wound around a sheave constituting the sheave pair of the secondary pulley and a sheave constituting the output sheave pair of the auxiliary pulley.

  According to the present invention, when transmitting the rotation of the primary pulley connected to the power source to the secondary pulley connected to the drive unit via the belt, the pulley diameters of the primary pulley and the secondary pulley are changed, respectively. In a belt-type continuously variable transmission that performs continuously variable transmission, an auxiliary pulley with a variable pulley diameter is interposed between the primary pulley and the secondary pulley between the primary pulley and the auxiliary pulley. In addition, the belt is wound between the auxiliary pulley and the secondary pulley, and the rotation of the primary pulley is transmitted to the secondary pulley in multiple stages via these belts, so that the pulley diameter of the primary pulley and the secondary pulley is extremely reduced. Wide change without making it small Range can be realized, it is possible to avoid a decrease in transmission efficiency due to belt slip loss.

BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows 1st Embodiment of the belt-type continuously variable transmission of this invention, (a) is a figure which shows an example of the system to which the belt-type continuously variable transmission was applied, (b) is (a). The figure seen from the axial direction of the rotating shaft shown to (c) is a figure which shows the state which removed the transmission belt from the primary pulley, secondary pulley, and auxiliary pulley which were shown to (a). It is a figure for demonstrating operation | movement of the belt-type continuously variable transmission shown in FIG. FIG. 2 is a diagram showing a state in which the power generated by the power source in the system shown in FIG. 1 is the largest and the rotation in the drive unit is the highest, (a) is a diagram showing the overall configuration, (b) These are the figures seen from the axial direction of the rotating shaft shown to (a). It is a figure for demonstrating the effect by the belt-type continuously variable transmission shown in FIGS. It is a figure for demonstrating the effect by the belt-type continuously variable transmission shown in FIGS. It is a figure which shows 2nd Embodiment of the belt-type continuously variable transmission of this invention, (a) is a figure which shows an example of the system with which the belt-type continuously variable transmission was applied, (b) is (a). The figure seen from the axial direction of the rotating shaft shown to (c) is a figure which shows the state which removed the transmission belt from the primary pulley, the secondary pulley, and auxiliary pulley which were shown to (a). It is a figure for demonstrating operation | movement of the belt-type continuously variable transmission shown in FIG. FIG. 7 is a diagram showing a state in which the power generated by the power source in the system shown in FIG. 6 is the largest and the rotation in the drive unit is the highest, (a) is a diagram showing the overall configuration, (b) These are the figures seen from the axial direction of the rotating shaft shown to (a). It is a figure which shows the other example of arrangement | positioning with the primary pulley in the belt-type continuously variable transmission shown in FIG.1 and FIG.6, a secondary pulley, and an auxiliary pulley.

  Embodiments of the present invention will be described below with reference to the drawings.

(First embodiment)
FIG. 1 is a diagram showing a first embodiment of a belt-type continuously variable transmission according to the present invention, (a) is a diagram showing an example of a system to which a belt-type continuously variable transmission is applied, and (b). (A) is a view seen from the axial direction of the rotary shafts 13, 23, 33 shown in (a), (c) is a transmission belt 41, 42 from the primary pulley 10, the secondary pulley 20 and the auxiliary pulley 30 shown in (a). It is a figure which shows the state removed.

  As shown in FIG. 1, the belt type continuously variable transmission according to the present embodiment includes a primary pulley 10 connected to a power source 50, a secondary pulley 20 connected to a drive unit 60, and an auxiliary pulley 30. .

  The power source 50 corresponds to an engine when the belt type continuously variable transmission of this embodiment is applied to an automobile. When the belt type continuously variable transmission according to the present embodiment is applied to an automobile, the drive unit 60 corresponds to a drive wheel, a reduction gear device, and the like, and is rotationally driven by the power generated by the power source 50. .

  The primary pulley 10 is connected to the power source 50 via the rotating shaft 13 and rotates around the rotating shaft 13 by the power generated by the power source 50. The primary pulley 10 has a sheave pair composed of a movable sheave 11 and a fixed sheave 12 that are opposed to each other on a rotating shaft 13. Each of the movable sheave 11 and the fixed sheave 12 has a certain thickness, and has a disk shape so that the outer diameters of the surfaces facing each other are reduced. The fixed sheave 12 is fixed to the rotating shaft 13 of the primary pulley 10, and the movable sheave 11 moves in the axial direction of the rotating shaft 13 by hydraulic control by the control unit 70, so that the movable sheave 11, the fixed sheave 12, , Thereby changing the pulley diameter of the primary pulley 10 in the region between the movable sheave 11 and the fixed sheave 12.

  The auxiliary pulley 30 rotates about a rotation shaft 33 that is parallel to the rotation shaft 13, and an input-side sheave pair that includes a fixed sheave 32 a and a variable sheave 31 a that are opposed to each other on the rotation shaft 13. It has an output sheave pair consisting of a fixed sheave 32b and a variable sheave 31b facing each other. Each of the movable sheave 31a and the fixed sheave 32a has a certain thickness and has a disk shape so that the outer diameters of the surfaces facing each other are reduced, and each of the movable sheave 31b and the fixed sheave 32b. Also, it has a disk-like shape that has a certain thickness and has a smaller outer diameter on the surfaces facing each other. The variable sheave 31a of the input side sheave pair and the variable sheave 31b of the output side sheave pair are integrated to form the movable sheave 31. In the input side sheave pair, the fixed sheave 32a is fixed to the rotating shaft 33 of the auxiliary pulley 30, and the movable sheave 31 moves in the axial direction of the rotating shaft 33, whereby the distance between the movable sheave 31a and the fixed sheave 32a. Changes, thereby changing the pulley diameter of the auxiliary pulley 30 in the region between the movable sheave 31a and the fixed sheave 32a. In the output side sheave pair, the fixed sheave 32b is fixed to the rotating shaft 33 of the auxiliary pulley 30, and the movable sheave 31 moves in the axial direction of the rotating shaft 33, whereby the distance between the movable sheave 31b and the fixed sheave 32b. Changes, thereby changing the pulley diameter of the auxiliary pulley 30 in the region between the movable sheave 31b and the fixed sheave 32b.

  The secondary pulley 20 is connected to the drive unit 60 via a rotation shaft 23 that is parallel to the rotation shaft 13 and rotates around the rotation shaft 23. The secondary pulley 20 has a sheave pair including a movable sheave 21 and a fixed sheave 22 that face each other on the rotating shaft 23. Each of the movable sheave 21 and the fixed sheave 22 has a certain thickness, and has a disk shape so that the outer diameters of the surfaces facing each other are reduced. The fixed sheave 22 is fixed to the rotating shaft 23 of the secondary pulley 20, and the movable sheave 21 moves in the axial direction of the rotating shaft 23, thereby changing the interval between the movable sheave 21 and the fixed sheave 22. The pulley diameter of the secondary pulley 20 in the region between the movable sheave 21 and the fixed sheave 22 changes.

  The primary pulley 10, the auxiliary pulley 30, and the secondary pulley 20 configured in this way are arranged in a straight line in this order in a direction orthogonal to the rotation shafts 13, 33, and 23. Further, the movable sheave 11 and the fixed sheave 12 of the primary pulley 10, the movable sheave 31 and the fixed sheaves 32a and 32b of the auxiliary pulley 30, and the movable sheave 21 and the fixed sheave 22 of the secondary pulley 20 have the same outer diameter. It has become a thing.

  Further, a transmission belt 41 serving as a first belt is provided between the movable sheave 11 and the fixed sheave 12 of the primary pulley 10 and between the movable sheave 31a and the fixed sheave 32a constituting the input-side sheave pair of the auxiliary pulley 30. It is wrapped around. Further, a transmission belt 42 serving as a second belt is provided between the movable sheave 21 and the fixed sheave 22 of the secondary pulley 20 and between the movable sheave 31b and the fixed sheave 32b constituting the output-side sheave pair of the auxiliary pulley 30. It is wrapped around.

  The operation of the belt type continuously variable transmission configured as described above will be described below.

  FIG. 2 is a view for explaining the operation of the belt type continuously variable transmission shown in FIG.

  First, when the power generated in the power source 50 starts to be transmitted to the drive unit 60, that is, when the rotation of the drive unit 60 is low, the primary pulley 10 has a movable sheave as shown in FIG. 11 is arranged at a position farthest from the fixed sheave 12. Further, in the auxiliary pulley 30, the movable sheave 31a is disposed at a position in contact with the fixed sheave 32a.

  As a result, in the primary pulley 10, the pulley diameter in the region between the movable sheave 11 and the fixed sheave 12 is due to the smallest outer diameter portion of the movable sheave 11 and the fixed sheave 12, and the input-side sheave of the auxiliary pulley 30. In the pair, the pulley diameter in the region between the movable sheave 31a and the fixed sheave 32a is due to the largest outer diameter portion of the movable sheave 31a and the fixed sheave 32a. As a result, as shown in FIG. 1, winding is performed between the movable sheave 11 and the fixed sheave 12 of the primary pulley 10 and between the movable sheave 31a and the fixed sheave 32a constituting the input-side sheave pair of the auxiliary pulley 30. The wound transmission belt 41 has a small winding diameter on the primary pulley 10 side and a large winding diameter on the auxiliary pulley 30 side.

  In addition, in the auxiliary pulley 30, the movable sheave 31a is disposed at a position in contact with the fixed sheave 32a, so that the movable sheave 31b integrated with the movable sheave 31a is located farthest from the fixed sheave 32b. It is in the state where it is arranged. Further, in the secondary pulley 20, the movable sheave 21 is arranged at a position in contact with the fixed sheave 22.

  Thereby, in the output side sheave pair of the auxiliary pulley 30, the pulley diameter in the region between the movable sheave 31b and the fixed sheave 32b is due to the smallest outer diameter portion of the movable sheave 31b and the fixed sheave 32b, and the secondary pulley 20, the pulley diameter in the region between the movable sheave 21 and the fixed sheave 22 is the largest outer diameter portion of the movable sheave 21 and the fixed sheave 22. As a result, as shown in FIG. 1, between the movable sheave 31b and the fixed sheave 32b constituting the output-side sheave pair of the auxiliary pulley 30, and between the movable sheave 21 and the fixed sheave 22 of the secondary pulley 20. The wound transmission belt 42 has a small winding diameter on the auxiliary pulley 30 side and a large winding diameter on the secondary pulley 20 side.

  Thereby, for example, the outer diameters of the movable sheave 11 and the fixed sheave 12 of the primary pulley 10, the movable sheave 31 and the fixed sheaves 32a and 32b of the auxiliary pulley 30, and the movable sheave 21 and the fixed sheave 22 of the secondary pulley 20 are the most. When the ratio of the diameter of the large portion to the diameter of the smallest portion is 1: 0.7, when the primary pulley 10 is rotated by the power generated by the power source 50, the rotation is transmitted via the belts 41 and 42. The rotation speed of the secondary pulley 20 transmitted to the secondary pulley 20 with respect to the primary pulley 10 is (0.7 × 0.7) /1≈0.5 times.

  When the power generated by the power source 50 is increased from this state, the movable sheave 11 of the primary pulley 10 is moved to the axis of the rotary shaft 13 by the hydraulic control of the control unit 70 as shown in FIG. It moves so as to approach the fixed sheave 12 in the direction.

  Then, the length of the transmission belt 41 is constant, between the movable sheave 11 of the primary sheave 10 and the fixed sheave 12, and the movable sheave 31a and the fixed sheave 32a that constitute the input-side sheave pair of the auxiliary pulley 30. Therefore, the movable sheave 31 of the auxiliary pulley 30 moves in the axial direction of the rotary shaft 33 so as to move away from the fixed sheave 32a and approach the fixed sheave 32b.

  Further, the transmission belt 42 has a constant length, between the movable sheave 31b and the fixed sheave 32b constituting the output-side sheave pair of the auxiliary pulley 30, and between the movable sheave 21 and the fixed sheave 22 of the secondary pulley 20. Since the movable sheave 31 of the auxiliary pulley 30 moves away from the fixed sheave 32a and approaches the fixed sheave 32b, the movable sheave 21 of the secondary pulley 20 is accordingly moved. It moves away from the fixed sheave 22 in the axial direction of the rotary shaft 23.

  When the power generated by the power source 50 becomes the largest and the rotation in the drive unit 60 becomes the highest, the movable sheave 11 contacts the fixed sheave 12 in the primary pulley 10 as shown in FIG. In the auxiliary pulley 30, the movable sheave 31 b is in a position in contact with the fixed sheave 32 b, and in the secondary pulley 20, the movable sheave 21 is the most from the fixed sheave 22. It becomes the state arrange | positioned in the distant position.

  FIG. 3 is a diagram showing a state in which the power generated by the power source 50 in the system shown in FIG. 1 is the largest and the rotation in the drive unit 60 is the highest, and (a) shows the overall configuration. The figure shown, (b) is the figure seen from the axial direction of the rotating shaft 13,23,33 shown to (a).

  When the power generated in the power source 50 is the largest and the rotation in the drive unit 60 is the highest, the pulley diameter in the region between the movable sheave 11 and the fixed sheave 12 is the movable pulley 11 and the primary pulley 10. In the input sheave pair of the auxiliary pulley 30, the pulley diameter in the region between the movable sheave 31a and the fixed sheave 32a is the largest of the movable sheave 31a and the fixed sheave 32a. This is due to the small outer diameter. As a result, as shown in FIG. 3, it is wound between the movable sheave 11 and the fixed sheave 12 of the primary pulley 10 and between the movable sheave 31a and the fixed sheave 32a constituting the input-side sheave pair of the auxiliary pulley 30. The transmitted belt 41 has a large winding diameter on the primary pulley 10 side and a small winding diameter on the auxiliary pulley 30 side.

  Further, in the output sheave pair of the auxiliary pulley 30, the pulley diameter in the region between the movable sheave 31b and the fixed sheave 32b is due to the largest outer diameter portion of the movable sheave 31b and the fixed sheave 32b, and the secondary pulley 20 The pulley diameter in the region between the movable sheave 21 and the fixed sheave 22 is due to the smallest outer diameter portion of the movable sheave 21 and the fixed sheave 22. As a result, as shown in FIG. 3, winding is performed between the movable sheave 31 b and the fixed sheave 32 b constituting the output-side sheave pair of the auxiliary pulley 30 and between the movable sheave 21 and the fixed sheave 22 of the secondary pulley 20. The hung transmission belt 42 has a large winding diameter on the auxiliary pulley 30 side and a small winding diameter on the secondary pulley 20 side.

  Thereby, for example, the outer diameters of the movable sheave 11 and the fixed sheave 12 of the primary pulley 10, the movable sheave 31 and the fixed sheaves 32a and 32b of the auxiliary pulley 30, and the movable sheave 21 and the fixed sheave 22 of the secondary pulley 20 are the most. When the ratio of the diameter of the large part to the diameter of the smallest part is 1: 0.7, the rotational speed of the secondary pulley 20 with respect to the primary pulley 10 is 1 / (0.7 × 0.7) ≈2 times. It becomes.

  As described above, the rotation of the primary pulley 10 due to the power generated by the power source 50 is transmitted to the secondary pulley 20 via the transmission belts 41 and 42 and the auxiliary pulley 30, and the secondary pulley 20 rotates. The drive unit 60 is rotationally driven by the power generated by the power source 50. At this time, the pulley diameters of the regions where the transmission belts 41 and 42 of the primary pulley 10, the auxiliary pulley 30, and the secondary pulley 20 are wound are respectively set. By changing as described above, the shift is automatically performed.

  Below, the effect by the auxiliary pulley 30 interposing between the primary pulley 10 and the secondary pulley 20 is demonstrated.

  4 and 5 are diagrams for explaining the effects of the belt-type continuously variable transmission shown in FIGS. In the figure, the speed change rate on the horizontal axis is the ratio of the distance between the movable sheave 21 and the fixed sheave 22 of the secondary pulley 20 (“0” when in contact, “100” when farthest away). In the figure, the transmission efficiency on the vertical axis indicates the rate at which the rotation of the primary pulley 10 is transmitted to the secondary pulley 20.

  When the auxiliary pulley 30 is not interposed between the primary pulley 10 and the secondary pulley 20 described above, the transmission efficiency is low in a region where the gear ratio is low and a region where the gear ratio is high, as indicated by a broken line in the figure. This is because, in the region where the gear ratio is low and the region where the gear ratio is high, as described above, the pulley diameter of one of the primary pulley 10 and the secondary pulley 20 becomes small. In the configuration in which the auxiliary pulley 30 is not interposed, the same speed range as the belt-type continuously variable transmission shown in FIGS. 1 to 3, that is, the rotational speed of the secondary pulley 20 relative to the primary pulley 10 is changed to 0.5 to 2 times. In order to achieve this, the ratio of the diameter of the largest part to the smallest part of the outer diameter of the movable sheave and the fixed sheave of each of the primary pulley and the secondary pulley needs to be 1: 0.25. By reducing the pulley diameter, the contact area with the transmission belt is further narrowed. More, because the transmission loss due to slippage loss occurs.

  On the other hand, in the belt-type continuously variable transmission shown in FIGS. 1 to 3, even if the rotational speed of the secondary pulley 20 relative to the primary pulley 10 is changed to 0.5 to 2 times as the speed change range, As described above, the outer diameters of the movable sheave 11 and the fixed sheave 12 of the primary pulley 10, the movable sheave 31 and the fixed sheaves 32 a and 32 b of the auxiliary pulley 30, and the movable sheave 21 and the fixed sheave 22 of the secondary pulley 20 are the largest. It is sufficient that the ratio of the diameter of the portion to the diameter of the smallest portion is 1: 0.7, so that the pulley diameter does not become so small even in the low speed region and the high speed region. As indicated by the solid line in the figure, transmission loss due to slip loss is unlikely to occur, and a decrease in transmission efficiency is suppressed.

  In addition, when a belt type continuously variable transmission is applied to an automobile, etc., in order to avoid a decrease in transmission efficiency in a region where the gear ratio is high, i.e., a region where the rotational speed of the drive unit is high, a variant pulley is adopted. Although it is conceivable to make the primary pulley diameter smaller than the secondary pulley diameter, in that case, in the region where the gear ratio is low, that is, in the region where the rotational speed of the drive unit is slow, the primary pulley diameter is considerably smaller. As a result, as indicated by a broken line in FIG. 5, the transmission efficiency is greatly reduced.

  On the other hand, in the belt type continuously variable transmission shown in FIGS. 1 to 3, as described above, the auxiliary pulley 30 is interposed between the primary pulley 10 and the secondary pulley 20, thereby adopting a variant pulley. Even if the diameter of the primary pulley is smaller than the diameter of the secondary pulley, it is not necessary to make the diameter of the primary pulley quite small even in a region where the gear ratio is low, that is, in a region where the rotational speed of the drive unit is slow. As shown by the solid line in FIG. 5, it is avoided that the transmission efficiency is greatly reduced.

  In this way, in order to compensate for the transmission efficiency greatly reduced in the region where the speed change rate is low, i.e., the region where the rotational speed of the drive unit is slow, it may be possible to provide a torque converter between the power source and the primary pulley. In that case, although the transmission efficiency can be improved by the torque converter itself, the transmission efficiency is lowered by the amount corresponding to the torque converter and the cost is increased. The same applies when an auxiliary transmission or the like is incorporated.

  On the other hand, in the belt type continuously variable transmission shown in FIGS. 1 to 3, only the auxiliary pulley 30 is interposed between the primary pulley 10 and the secondary pulley 20. Compared to the cost increase. Moreover, the thing which has a comparatively small pulley diameter as the primary pulley 10, the secondary pulley 20, and the auxiliary pulley 30 can be employ | adopted, and the freedom degree of the layout of a drive system can be improved.

  As described above, in this embodiment, when the rotation of the primary pulley 10 connected to the power source 50 is transmitted to the secondary pulley 20 connected to the driving unit 60 via the transmission belt, the primary pulley 10 and the secondary pulley are transmitted. In the case of continuously variable transmission by changing the pulley diameter of each of the 20 pulleys, an auxiliary pulley 30 having a variable pulley diameter is interposed between the primary pulley 10 and the secondary pulley 20 in the same manner as the primary pulley 10 and the secondary pulley 20. The transmission belts 41 and 42 are wound between the primary pulley 10 and the auxiliary pulley 30 and between the auxiliary pulley 30 and the secondary pulley 20, respectively, and the rotation of the primary pulley 10 is caused to rotate these transmission belts 41 and 42. To the secondary pulley 20 in multiple stages By reaching, you can realize a wide speed range without extremely small pulley diameters of the primary pulley 10 and secondary pulley 20, can avoid a decrease in transmission efficiency due to belt slip loss.

  Further, the variable sheave 31a of the input sheave pair of the auxiliary pulley 30 and the variable sheave 31b of the output sheave pair are integrated to form the movable sheave 31, so that the primary pulley 10 is controlled by hydraulic control of the control unit 70. By only moving the movable pulley 11, not only the movable sheave 31 a of the auxiliary pulley 30 but also the movable sheave 21 of the secondary pulley 20 can be moved via the movable sheave 31 b of the auxiliary pulley 30.

(Second Embodiment)
FIG. 6 is a diagram showing a belt type continuously variable transmission according to a second embodiment of the present invention. FIG. 6A is a diagram showing an example of a system to which a belt type continuously variable transmission is applied. FIG. (A) is a view seen from the axial direction of the rotating shafts 13, 23, 33 shown in (a), (c) is a transmission belt 41, 42 from the primary pulley 10, the secondary pulley 20 and the auxiliary pulley 30 shown in (a). It is a figure which shows the state removed.

  As shown in FIG. 6, the belt type continuously variable transmission according to the present embodiment has a variable sheave 31a of the input sheave pair and a variable sheave 31b of the output sheave pair of the auxiliary pulley 30. It is different in that it is not integrated but separated. Therefore, in addition to the controller 70a that hydraulically controls the movement of the movable pulley 11 of the primary pulley 10, the controller 70b that hydraulically controls the movement of the movable pulley 21 of the secondary pulley 20 is provided. Note that the controller 70b does not hydraulically control the movement of the movable pulley 21 of the secondary pulley 20, but may hydraulically control the movement of the movable pulley 31b of the auxiliary pulley 30.

  The operation of the belt type continuously variable transmission configured as described above will be described below.

  FIG. 7 is a diagram for explaining the operation of the belt type continuously variable transmission shown in FIG.

  First, when the power generated by the power source 50 starts to be transmitted to the drive unit 60, that is, when the rotation of the drive unit 60 is low, the primary pulley 10 has a movable sheave as shown in FIG. 11 is arranged at a position farthest from the fixed sheave 12. Further, in the auxiliary pulley 30, the movable sheave 31a is disposed at a position in contact with the fixed sheave 32a.

  As a result, in the primary pulley 10, the pulley diameter in the region between the movable sheave 11 and the fixed sheave 12 is due to the smallest outer diameter portion of the movable sheave 11 and the fixed sheave 12, and the input-side sheave of the auxiliary pulley 30. In the pair, the pulley diameter in the region between the movable sheave 31a and the fixed sheave 32a is due to the largest outer diameter portion of the movable sheave 31a and the fixed sheave 32a. As a result, as shown in FIG. 6, winding is performed between the movable sheave 11 and the fixed sheave 12 of the primary pulley 10 and between the movable sheave 31a and the fixed sheave 32a constituting the input-side sheave pair of the auxiliary pulley 30. The wound transmission belt 41 has a small winding diameter on the primary pulley 10 side and a large winding diameter on the auxiliary pulley 30 side.

  Further, in the auxiliary pulley 30, the movable sheave 31b is disposed at the position farthest from the fixed sheave 32b. Further, in the secondary pulley 20, the movable sheave 21 is arranged at a position in contact with the fixed sheave 22.

  Thereby, in the output side sheave pair of the auxiliary pulley 30, the pulley diameter in the region between the movable sheave 31b and the fixed sheave 32b is due to the smallest outer diameter portion of the movable sheave 31b and the fixed sheave 32b, and the secondary pulley 20, the pulley diameter in the region between the movable sheave 21 and the fixed sheave 22 is the largest outer diameter portion of the movable sheave 21 and the fixed sheave 22. As a result, as shown in FIG. 6, between the movable sheave 31b and the fixed sheave 32b constituting the output-side sheave pair of the auxiliary pulley 30, and between the movable sheave 21 and the fixed sheave 22 of the secondary pulley 20. The wound transmission belt 42 has a small winding diameter on the auxiliary pulley 30 side and a large winding diameter on the secondary pulley 20 side.

  Thereby, for example, the outer diameters of the movable sheave 11 and the fixed sheave 12 of the primary pulley 10, the movable sheaves 31 a and 31 b and the fixed sheaves 32 a and 32 b of the auxiliary pulley 30, and the movable sheave 21 and the fixed sheave 22 of the secondary pulley 20. When the ratio of the diameter of the largest part to the diameter of the smallest part is 1: 0.7, when the primary pulley 10 is rotated by the power generated by the power source 50, the rotation causes the belts 41 and 42 to rotate. And the rotational speed of the secondary pulley 20 with respect to the primary pulley 10 is (0.7 × 0.7) /1≈0.5 times.

  When the power generated by the power source 50 increases from this state, as shown in FIG. 7B, the primary pulley 10 is controlled by the hydraulic control of the control unit 70a as shown in FIG. 7B. The movable sheave 11 moves in the axial direction of the rotary shaft 13 so as to approach the fixed sheave 12.

  Then, the length of the transmission belt 41 is constant, between the movable sheave 11 of the primary sheave 10 and the fixed sheave 12, and the movable sheave 31a and the fixed sheave 32a that constitute the input-side sheave pair of the auxiliary pulley 30. Therefore, the movable sheave 31a of the auxiliary pulley 30 moves in the axial direction of the rotary shaft 33 so as to move away from the fixed sheave 32a and approach the fixed sheave 32b.

  Further, the movable sheave 21 of the secondary pulley 20 moves away from the fixed sheave 22 in the axial direction of the rotating shaft 23 by hydraulic control of the control unit 70b.

  Then, the length of the transmission belt 42 is constant, between the movable sheave 21 and the fixed sheave 22 of the secondary sheave 20, and the movable sheave 31b and the fixed sheave 32b that constitute the output-side sheave pair of the auxiliary pulley 30. Therefore, the movable sheave 31b of the auxiliary pulley 30 moves in the axial direction of the rotary shaft 33 so as to approach the fixed sheave 32b.

  When the power generated by the power source 50 becomes the largest and the rotation in the drive unit 60 becomes the highest, the movable sheave 11 contacts the fixed sheave 12 in the primary pulley 10 as shown in FIG. In the auxiliary pulley 30, the movable sheave 31a is disposed at a position farthest from the fixed sheave 32a, and the movable sheave 31b is disposed at a position in contact with the fixed sheave 32b. In addition, in the secondary pulley 20, the movable sheave 21 is arranged at a position farthest from the fixed sheave 22.

  FIG. 8 is a diagram showing a state in which the power generated by the power source 50 is the largest in the system shown in FIG. 6 and the rotation in the drive unit 60 is the highest, and (a) shows the overall configuration. The figure shown, (b) is the figure seen from the axial direction of the rotating shaft 13,23,33 shown to (a).

  When the power generated in the power source 50 is the largest and the rotation in the drive unit 60 is the highest, the pulley diameter in the region between the movable sheave 11 and the fixed sheave 12 is the movable pulley 11 and the primary pulley 10. In the input sheave pair of the auxiliary pulley 30, the pulley diameter in the region between the movable sheave 31a and the fixed sheave 32a is the largest of the movable sheave 31a and the fixed sheave 32a. This is due to the small outer diameter. As a result, as shown in FIG. 8, it is wound between the movable sheave 11 and the fixed sheave 12 of the primary pulley 10 and between the movable sheave 31a and the fixed sheave 32a constituting the input-side sheave pair of the auxiliary pulley 30. The transmitted belt 41 has a large winding diameter on the primary pulley 10 side and a small winding diameter on the auxiliary pulley 30 side.

  Further, in the output sheave pair of the auxiliary pulley 30, the pulley diameter in the region between the movable sheave 31b and the fixed sheave 32b is due to the largest outer diameter portion of the movable sheave 31b and the fixed sheave 32b, and the secondary pulley 20 The pulley diameter in the region between the movable sheave 21 and the fixed sheave 22 is due to the smallest outer diameter portion of the movable sheave 21 and the fixed sheave 22. As a result, as shown in FIG. 8, it is wound between the movable sheave 21 and the fixed sheave 22 of the secondary pulley 20 and between the movable sheave 31b and the fixed sheave 32b constituting the output-side sheave pair of the auxiliary pulley 30. The transmitted belt 42 has a large winding diameter on the auxiliary pulley 30 side and a small winding diameter on the secondary pulley 20 side.

  Thereby, for example, the outer diameters of the movable sheave 11 and the fixed sheave 12 of the primary pulley 10, the movable sheaves 31 a and 31 b and the fixed sheaves 32 a and 32 b of the auxiliary pulley 30, and the movable sheave 21 and the fixed sheave 22 of the secondary pulley 20. When the ratio of the diameter of the largest part to the diameter of the smallest part is 1: 0.7, the rotational speed of the secondary pulley 20 with respect to the primary pulley 10 is 1 / (0.7 × 0.7) ≈ Doubled.

  As described above, the rotation of the primary pulley 10 due to the power generated by the power source 50 is transmitted to the secondary pulley 20 via the transmission belts 41 and 42 and the auxiliary pulley 30, and the secondary pulley 20 rotates. The drive unit 60 is rotationally driven by the power generated by the power source 50, and at that time, the pulley diameters of the primary pulley 10, the auxiliary pulley 30, and the secondary pulley 20 are changed automatically as described above. Will be done.

  In this embodiment, the variable sheave 31a of the input-side sheave pair of the auxiliary pulley 30 and the variable sheave 31b of the output-side sheave pair are not integrated, but are separated, so that the input-side sheave pair is variable. The interval between the sheave 31a and the fixed sheave 32a and the interval between the variable sheave 31b and the fixed sheave 32b of the output-side sheave pair can be independently changed, and more detailed shift timing and shift rate control can be performed. It becomes possible.

  In the embodiment described above, the primary pulley 10, the auxiliary pulley 30, and the secondary pulley 20 are arranged in a straight line in this order in a direction orthogonal to the rotation shafts 13, 33, 23. The arrangement is not limited to a linear arrangement as long as the auxiliary pulley 20 is interposed between the primary pulley 10 and the secondary pulley 20.

  FIG. 9 is a view showing another example of the arrangement of the primary pulley 10, the secondary pulley 20, and the auxiliary pulley 30 in the belt type continuously variable transmission shown in FIG. 1 and FIG. It is the figure seen from the axial direction.

  The primary pulley 10, the auxiliary pulley 30, and the secondary pulley 20 shown in FIG. 1 and FIG. 6 are not arranged in a straight line in the direction orthogonal to the rotation shafts 13, 33, 23, but as shown in FIG. Moreover, when viewed from the axial direction of the rotary shafts 13, 33, 23, they may be arranged in a triangle shape. Even in this case, the transmission belt 41 is wound around the primary pulley 10 and the auxiliary pulley 30, and the transmission belt 42 is wound between the auxiliary pulley 30 and the secondary pulley 20.

  As in the case shown in FIGS. 1 and 6, when the power generated by the power source 50 starts to be transmitted to the drive unit 60, that is, when the rotation of the drive unit 60 is low, FIG. As shown, the transmission belt 41 wound around the primary pulley 10 and the auxiliary pulley 30 has a small winding diameter on the primary pulley 10 side and a large winding diameter on the auxiliary pulley 30 side. The transmission belt 42 wound around the auxiliary pulley 30 and the secondary pulley 20 has a small winding diameter on the auxiliary pulley 30 side and a large winding diameter on the secondary pulley 20 side.

  After that, when the power generated in the power source 50 becomes the largest and the rotation in the drive unit 60 becomes the highest, the transmission belt wound around the primary pulley 10 and the auxiliary pulley 30 as shown in FIG. 9C. 41 has a large winding diameter on the primary pulley 10 side and a small winding diameter on the auxiliary pulley 30 side, and the transmission belt 42 wound around the auxiliary pulley 30 and the secondary pulley 20 The winding diameter is large on the pulley 30 side, and the winding diameter is small on the secondary pulley 20 side.

  In this way, even when the primary pulley 10, the auxiliary pulley 30, and the secondary pulley 20 are arranged as shown in FIG. 9, the rotation of the primary pulley 10 by the power generated by the power source 50 is transmitted to the transmission belt 41, 42 and the auxiliary pulley 30 are transmitted to the secondary pulley 20 and the secondary pulley 20 is rotated, so that the driving unit 60 is rotationally driven by the power generated by the power source 50. In this case, the primary pulley 10, As the pulley diameters of the auxiliary pulley 30 and the secondary pulley 20 change as described above, a shift is automatically performed.

  In the above-described embodiment, the configuration in which one auxiliary pulley 30 is interposed between the primary pulley 10 and the secondary pulley 20 has been described as an example. However, the configuration between the primary pulley 10 and the secondary pulley 20 is described. A plurality of auxiliary pulleys 30 may be interposed. In that case, the transmission belt is also wound between the plurality of auxiliary pulleys, and the rotation of the primary pulley 10 is wound between the transmission belt wound between the primary pulley and the auxiliary pulley and the plurality of auxiliary pulleys. The transmission belt is transmitted to the secondary pulley 20 via the transmission belt and the transmission belt wound between the auxiliary pulley and the secondary pulley 20.

  The belt type continuously variable transmission described above can be applied to industrial machine tools and the like in addition to small displacement motorcycles and automobiles. In that case, it is possible to avoid a decrease in transmission efficiency in each of the high speed and low speed areas of the drive unit, thereby improving the climbing performance in automobiles and the like, and the start performance of small-displacement motorcycles, and also maintaining high rotation It can be expected to improve fuel economy at the time.

DESCRIPTION OF SYMBOLS 10 Primary pulley 11, 21, 31, 31a, 31b Movable sheave 12, 22, 32a, 32b Fixed sheave 13,23,33 Rotating shaft 20 Secondary pulley 30 Auxiliary pulley 41, 42 Transmission belt 50 Power source 60 Drive part 70, 70a 70b Control unit

Claims (4)

A primary pulley connected to a power source and having a variable pulley diameter;
A secondary pulley that is coupled to a drive unit that is rotationally driven by power generated by the power source, and the pulley diameter is variable;
And at least one auxiliary pulley having a variable pulley diameter is arranged such that its rotation axes are parallel to each other,
Belts are respectively wound between the primary pulley and the auxiliary pulley, and between the auxiliary pulley and the secondary pulley, and when there are a plurality of the auxiliary pulleys, the belt is also interposed between the plurality of auxiliary pulleys. Is a belt type continuously variable transmission that transmits the rotation of the primary pulley to the secondary pulley via the belt. A primary pulley having a sheave pair connected to a power source and changing a pulley diameter in a region between each other by changing a distance between each other;
A secondary pulley that is connected to a drive unit that is rotationally driven by power generated by the power source, and includes a sheave pair that changes a pulley diameter in a region between each other by changing a distance between each other;
An auxiliary pulley having an input sheave pair and an output sheave pair that change the pulley diameter in a region between each other by changing the distance between them is arranged so that the rotation axes thereof are parallel to each other,
A first belt wound between sheaves constituting the sheave pair of the primary pulley and between sheaves constituting the input-side sheave pair of the auxiliary pulley;
A belt-type continuously variable transmission having a second belt wound between sheaves constituting the sheave pair of the secondary pulley and between sheaves constituting the output-side sheave pair of the auxiliary pulley. The belt type continuously variable transmission according to claim 2,
Each of the input sheave pair and the output sheave pair includes a fixed sheave fixed to the auxiliary pulley and a movable sheave movable in the axial direction of the auxiliary pulley.
A belt type continuously variable transmission in which the movable sheave of the input side sheave pair and the movable sheave of the output side sheave pair are integrated. The belt type continuously variable transmission according to claim 2,
The input-side sheave pair and the output-side sheave pair are belt-type continuously variable transmissions in which the distance between the sheaves changes independently.

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