JP2004257468A - Belt-type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To easily realize cost reduction of a belt type continuously variable transmission, and at the same time, to excellently stabilize operations of a movable sheave of the continuously variable transmission. <P>SOLUTION: The movable sheave 38 of the belt type continuously variable transmission 9 allows the axial movement of the movable sheave 38 to a primary shaft SP. While, the movable sheave 38 is provided to a spline 38s for regulating the rotation of the movable sheave 38 to the primary shaft SP, on the side of the spline 38s in the axial direction of the primary shaft SP, and on the inner peripheral face of the movable sheave 38. It is also provided to a first sliding part 38c coming into contact with the outer peripheral face of the primary shaft SP, on the opposite side of the first sliding part 38c across the spline 38s, and on the outer peripheral face of the movable sheave 38. It is provided with a second sliding part 38d coming into contact with the inner peripheral face of a partition wall member 70. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a belt-type continuously variable transmission that can obtain a desired gear ratio by changing a winding radius of a belt.
[0002]
[Prior art]
BACKGROUND ART Conventionally, a belt-type continuously variable transmission has been known as a transmission for a vehicle (for example, see Patent Document 1). This type of belt-type continuously variable transmission includes a primary shaft (drive-side rotating shaft) and a secondary shaft (driven-side rotating shaft) arranged in parallel with each other, a primary pulley mounted on the primary shaft, and a secondary pulley mounted on the secondary shaft. Secondary pulley. Each of the primary pulley and the secondary pulley includes a fixed sheave and a movable sheave movable with respect to the fixed sheave. Further, each movable sheave is movable axially but not circumferentially with respect to the corresponding rotating shaft via a ball and a ball groove (ball spline). A substantially V-shaped pulley groove is formed between the fixed sheave and the movable sheave, and an endless belt is wound around each of the pulley grooves of the primary pulley and the secondary pulley. In addition, an oil chamber is provided for the primary pulley and the secondary pulley so that each movable sheave approaches and separates from the corresponding fixed sheave. The oil pressure in each oil chamber is separately controlled, thereby changing the groove width of the pulley, changing the winding radius of the belt, setting the gear ratio to a desired value, and adjusting the belt tension. .
[0003]
[Patent Document 1]
JP 2001-323978 A
[0004]
[Problems to be solved by the invention]
In order to operate the above-mentioned movable sheave stably, it is necessary to provide sliding portions at both axial ends of the ball spline. However, conventionally, it has been difficult to form a ball spline due to the existence of the sliding portion.
[0005]
Therefore, an object of the present invention is to provide a belt-type continuously variable transmission that can easily form splines and can stably operate the movable sheave.
[0006]
[Means for Solving the Problems]
A belt-type continuously variable transmission according to the present invention includes a movable sheave and a fixed sheave arranged on the outer periphery of a rotating shaft, and a belt wound around the movable sheave and the fixed sheave, and moves the movable sheave with respect to the fixed sheave. In the belt-type continuously variable transmission that can obtain a desired gear ratio by changing the winding radius of the belt, the movable sheave allows the movable sheave to move in the axial direction with respect to the rotation shaft, while the movable sheave A spline that regulates rotation of the movable sheave, and a first sliding portion that is provided on a side of the spline in the axial direction of the rotation shaft and on an inner peripheral portion of the movable sheave and that contacts an outer peripheral surface of the rotation shaft. A second sliding portion, which is provided on the opposite side of the first sliding portion with respect to the spline and on the outer peripheral portion of the movable sheave, and is in contact with members other than the rotating shaft. The features.
[0007]
In this belt-type continuously variable transmission, the movable sheave disposed on the outer periphery of at least one of the drive-side and driven-side rotation shafts allows the movable sheave to move in the axial direction with respect to the rotation shaft, while moving with respect to the rotation shaft. It has a spline that regulates the rotation of the sheave. The movable sheave has first and second sliding portions on both sides of the spline in the axial direction of the rotation shaft. The first sliding portion of the first and second sliding portions of the movable sheave is provided on the inner peripheral portion of the movable sheave and contacts the outer peripheral surface of the rotating shaft, while the second sliding portion contacts the outer peripheral surface of the rotating shaft. The portion is provided on the outer peripheral portion of the movable sheave and comes into contact with members other than the rotation shaft.
[0008]
As described above, the second sliding portion is provided on the outer peripheral portion of the movable sheave so as to be in contact with a member other than the rotary shaft, so that when the spline is formed on the movable sheave, the second sliding portion is broached. It can be prevented that the movement of the tool such as is hindered. Therefore, by performing machining with a tool such as a broach from one sliding portion side to the other sliding portion side, it is possible to extremely easily form splines on the movable sheave in a short time. . In addition, in this continuously variable transmission, since the sliding portions are secured on both sides of the spline in the axial direction of the rotating shaft, the operation of the movable sheave with respect to the rotating shaft can be stabilized very well.
[0009]
In this case, it is preferable that members other than the rotating shaft are partition members that define an oil chamber for applying hydraulic pressure to the movable sheave.
[0010]
Another belt-type continuously variable transmission according to the present invention includes a movable sheave and a fixed sheave arranged on the outer periphery of a rotating shaft, and a belt wound around the movable sheave and the fixed sheave. A belt-type continuously variable transmission that can obtain a desired gear ratio by changing the winding radius of the belt by moving the belt has a cylindrical portion that covers the outer periphery of the rotating shaft, and is fixed to the rotating shaft. The movable sheave allows the axial movement of the movable sheave with respect to the rotation axis, while restricting the rotation of the movable sheave with respect to the rotation axis, and a side of the spline in the axial direction of the rotation axis, and A first sliding portion provided on an inner peripheral portion of the movable sheave and in contact with an outer peripheral surface of the rotating shaft; and a movable sliding member opposite to the first sliding portion with the spline interposed therebetween. Provided on the inner peripheral portion of the probe, characterized in that it comprises a second sliding portion in contact with the outer peripheral surface of the cylindrical portion of the member fixed to the rotating shaft.
[0011]
This belt-type continuously variable transmission includes a member that has a cylindrical portion that covers an outer periphery of at least one of the drive-side and driven-side rotation shafts and is fixed to the rotation shaft. The movable sheave of this continuously variable transmission also has first and second sliding portions on both sides of the spline in the axial direction of the rotating shaft. The first and second sliding portions of the movable sheave are both provided on the inner peripheral portion of the movable sheave, and the first sliding portion contacts the outer peripheral surface of the rotating shaft while the second sliding portion is in contact with the outer peripheral surface of the rotating shaft. The portion contacts the outer peripheral surface of the cylindrical portion of the member fixed to the rotation shaft.
[0012]
As described above, by configuring the second sliding portion to be in contact with the cylindrical portion of the member fixed to the rotating shaft, the inner diameter of the second sliding portion is substantially smaller than the outer diameter of the rotating shaft. Can be increased by the thickness of the movable sheave, and it is possible to prevent the second sliding portion from hindering movement of a tool such as a broach when forming a spline in the movable sheave. Therefore, by performing machining with a tool such as a broach from one sliding portion side to the other sliding portion side, it is possible to extremely easily form splines on the movable sheave in a short time. . Also in this continuously variable transmission, the sliding portions are secured on both sides of the spline in the axial direction of the rotating shaft, so that the operation of the movable sheave with respect to the rotating shaft can be stabilized very well.
[0013]
In this case, the member fixed to the rotation shaft is preferably a partition member that defines an oil chamber for applying a hydraulic pressure to the movable sheave.
[0014]
Still another belt-type continuously variable transmission according to the present invention includes a movable sheave and a fixed sheave arranged on the outer periphery of a rotating shaft, and a belt wound around the movable sheave and the fixed sheave. In contrast, in a belt-type continuously variable transmission that can obtain a desired gear ratio by changing the winding radius of the belt by moving the movable sheave, the movable sheave allows axial movement of the movable sheave with respect to the rotating shaft, A spline that regulates rotation of the movable sheave with respect to the rotating shaft; A movable portion and an inner peripheral portion of the movable sheave and an axially outermost portion of the movable sheave on the opposite side of the first sliding portion with respect to the spline; And a second sliding portion in contact with, this second sliding portion, and a plurality of grooves extending parallel to the spline is formed.
[0015]
The movable sheave of this belt type continuously variable transmission also has first and second sliding portions on both sides of the spline in the axial direction of the rotation shaft. The first and second sliding portions of the movable sheave are both provided on the inner peripheral portion of the movable sheave and contact the outer peripheral surface of the rotating shaft, respectively. And a plurality of grooves extending therethrough. Under such a configuration, by performing machining from one sliding portion side to the other sliding portion side with a tool such as a broach, the spline can be formed at low cost together with the groove of the second sliding portion. It can be formed very easily in a short time. Also in this continuously variable transmission, the sliding portions are secured on both sides of the spline in the axial direction of the rotating shaft, and the second sliding portion can be effectively provided up to the extreme end of the movable sheave, so that the rotation can be reduced. The operation of the movable sheave with respect to the shaft can be stabilized very well.
[0016]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, preferred embodiments of a belt-type continuously variable transmission according to the present invention will be described in detail with reference to the drawings.
[0017]
[First Embodiment]
FIG. 1 is a schematic configuration diagram showing a vehicle to which a belt-type continuously variable transmission according to a first embodiment of the present invention is applied. The vehicle 1 shown in FIG. 1 is configured as a so-called FF vehicle (front engine front drive: front-wheel drive vehicle with an engine installed) and includes an engine 2 as a drive source. As the engine 2, a gasoline engine, a diesel engine, an LPG engine, a hydrogen engine, a bi-fuel engine, or the like can be employed. Here, a description will be given assuming that a gasoline engine is used as the engine 2.
[0018]
As shown in FIG. 1, the vehicle 1 has a transaxle 3 that is arranged on a side of the engine 2 placed in a horizontal position and is connected to a crankshaft SC of the engine 2. The transaxle 3 includes a transaxle housing 4, a transaxle case 5, and a transaxle rear cover 6. The housing 4 is arranged on the side of the engine 2, and the case 5 is fixed to an open end of the housing 4 opposite to the engine 2. The rear cover 6 is fixed to an open end of the case 5 on the side opposite to the housing 4. A torque converter 7 is disposed inside the transaxle housing 4, and a forward / reverse switching mechanism 8 is provided inside the transaxle case 5 and the transaxle rear cover 6, and the belt according to the first embodiment of the present invention. A continuously variable transmission (CVT) 9 and a final reduction gear (differential device) 10 are arranged.
[0019]
The torque converter 7 has a drive plate 11 and a front cover 12 fixed to the crankshaft SC of the engine 2 via the drive plate 11. A pump impeller 14 is attached to the front cover 12, as shown in FIG. Further, torque converter 7 includes a turbine runner 15 rotatable in a state facing pump impeller 14.
[0020]
The turbine runner 15 is fixed to an input shaft SI extending substantially coaxially with the crankshaft SC. Further, a stator 16 is arranged inside the pump impeller 14 and the turbine runner 15, and the rotation direction of the stator 16 is set by the one-way clutch 17 in only one direction. A hollow shaft 18 is fixed to the stator 16 via a one-way clutch 17, and the above-described input shaft SI is inserted into the hollow shaft 18. A lock-up clutch 20 is attached to an end of the input shaft SI on the front cover 12 side via a damper mechanism 19.
[0021]
The above-described pump impeller 14, turbine runner 15, and stator 16 define a working fluid chamber, which is operated by an oil pump 21 disposed between the torque converter 7 and the forward / reverse switching mechanism 8. Liquid is supplied. Then, when the engine 2 operates and the front cover 12 and the pump impeller 14 rotate, the turbine runner 15 starts rotating so that the flow of the hydraulic fluid causes the turbine runner 15 to be dragged. Further, when the rotation speed difference between the pump impeller 14 and the turbine runner 15 is large, the stator 16 converts the flow of the working fluid into a direction that assists the rotation of the pump impeller 14.
[0022]
Thereby, the torque converter 7 operates as a torque amplifier when the rotation speed difference between the pump impeller 14 and the turbine runner 15 is large, and operates as a fluid coupling when the rotation speed difference between the two is small. When the vehicle speed reaches a predetermined speed after the vehicle 1 starts moving, the lock-up clutch 20 is operated so that the power transmitted from the engine 2 to the front cover 12 is mechanically and directly transmitted to the input shaft SI. Become. Further, the fluctuation of the torque transmitted from the front cover 12 to the input shaft SI is absorbed by the damper mechanism 19.
[0023]
The oil pump 21 between the torque converter 7 and the forward / reverse switching mechanism 8 has a rotor 22, which is connected to the pump impeller 14 via a hub 23. Further, the hub 23 is spline-fitted to the hollow shaft 18, and the main body 24 of the oil pump 21 is fixed to the transaxle case 5 side. Therefore, the power of the engine 2 is transmitted to the rotor 22 via the pump impeller 14, whereby the oil pump 21 is driven.
[0024]
The forward / reverse switching mechanism 8 has a double pinion type planetary gear mechanism 25. The planetary gear mechanism 25 includes a sun gear 26 attached to an end of the input shaft SI on the side of the continuously variable transmission 9, a ring gear 27 concentrically arranged on the outer peripheral side of the sun gear 26, and a plurality of pinion gears meshing with the sun gear 26. 28, a plurality of pinion gears 29 that mesh with both the ring gear 27 and the pinion gear 28, and a carrier 30 that holds each of the pinion gears 28 so as to be able to rotate, and holds the pinion gears 28 so that they can revolve integrally around the sun gear 26. And
[0025]
The carrier 30 of the forward / reverse switching mechanism 8 is fixed to a primary shaft SP included in the belt-type continuously variable transmission 9, and a power transmission path between the carrier 30 and the input shaft SI is connected or connected using a forward clutch CR. Will be shut off. The forward / reverse switching mechanism 8 has a reverse brake BR for controlling rotation and fixing of the ring gear 27.
[0026]
On the other hand, the belt-type continuously variable transmission 9 according to the first embodiment of the present invention is configured so that the above-described primary shaft (drive-side rotation shaft) SP extending substantially coaxially with the input shaft SI is parallel to the primary shaft SP. And a secondary shaft (driven-side rotation shaft) SS arranged. The primary shaft SP is rotatably supported by bearings 31 and 32, and the secondary shaft SS is rotatably supported by bearings 33 and. The primary shaft SP is equipped with a primary pulley 35, and the secondary shaft SS is equipped with a secondary pulley 36.
[0027]
The primary pulley 35 includes a fixed sheave 37 integrally formed on the outer periphery of the primary shaft SP, and a movable sheave 38 slidably mounted on the outer periphery of the primary shaft SP. The fixed sheave 37 and the movable sheave 38 face each other, and a substantially V-shaped pulley groove 39 is formed therebetween. Further, the movable sheave 38 is movable in the axial direction of the primary shaft SP with respect to the fixed sheave 37, and the continuously variable transmission 9 moves the movable sheave 38 in the axial direction of the primary shaft SP to A hydraulic actuator 40 is provided to move the fixed sheave 37 toward and away from the fixed sheave 37.
[0028]
Similarly, the secondary pulley 36 also includes a fixed sheave 41 integrally formed on the outer periphery of the secondary shaft SS, and a movable sheave 42 slidably mounted on the outer periphery of the secondary shaft SS. The fixed sheave 41 and the movable sheave 42 face each other, and a substantially V-shaped pulley groove 44 is formed between them. The movable sheave 42 is also movable in the axial direction of the secondary shaft SS with respect to the fixed sheave 41, and the continuously variable transmission 9 moves the movable sheave 42 in the axial direction of the secondary shaft SS to A hydraulic actuator 45 is provided to move the fixed sheave 41 toward and away from the fixed sheave 41.
[0029]
A belt B composed of a large number of metal pieces and a plurality of steel rings is wound around the pulley groove 39 of the primary pulley 35 and the pulley groove 44 of the secondary pulley 36 described above. Then, the hydraulic pressures of the hydraulic actuators 40 and 45 are separately controlled, whereby the groove width of the primary pulley 35 and the secondary pulley 36 is changed, and the winding radius of the belt B is changed. As a result, the speed ratio of the continuously variable transmission 9 is set to a desired value, and the tension of the belt B is adjusted. Note that a bearing 34 that supports the secondary shaft SS is fixed to the transaxle rear cover 6, and a parking gear PG is provided between the bearing 34 and the secondary pulley 36.
[0030]
As shown in FIG. 1, a shaft 48 supported by bearings 46 and 47 is connected to the secondary shaft SS of the belt-type continuously variable transmission 9. A counter driven gear 49 is fixed to the shaft 48, and power is transmitted from the belt-type continuously variable transmission 9 to the final reduction gear 10 via the counter driven gear 49. The final reduction gear 10 includes an intermediate shaft 50 arranged so as to be parallel to the secondary shaft SS. The intermediate shaft 50 is supported by bearings 51 and 52, and a counter driven gear 53 that meshes with the counter driven gear 49 of the secondary shaft SS, and a final drive gear 54 are fixed to the shaft 50.
[0031]
Further, the final reduction gear 10 has a hollow differential case 55. The differential case 55 is rotatably supported by bearings 56 and 57, and a ring gear 58 is formed on the outer periphery thereof. The ring gear 58 meshes with the final drive gear 54 of the intermediate shaft 50. Further, the differential case 55 supports a pinion shaft 59 therein, and two pinion gears 60 are fixed to the pinion shaft 59. Two side gears 61 are meshed with each pinion gear 60, and a front drive shaft 62 is separately connected to each side gear 61, and a wheel (front wheel) FW is fixed to each front drive shaft 62. ing.
[0032]
FIG. 2 is an enlarged cross-sectional view showing a main part of the belt-type continuously variable transmission 9 according to the present invention included in the vehicle 1 described above, and shows the primary pulley 35 and the primary shaft of the continuously variable transmission 9. 2 shows a configuration related to the SP. As shown in FIGS. 2 and 3, in the belt-type continuously variable transmission 9, a plurality of (in this embodiment, a total of 30) splines (teeth) 38 s are formed on the inner peripheral surface of the movable sheave 38. . A plurality of spline grooves SPg that mesh with the splines 38s of the movable sheave 38 are formed on the outer peripheral surface of the primary shaft SP that slidably supports the movable sheave 38.
[0033]
The spline 38s of the movable sheave 38 and the spline groove SPg of the primary shaft SP are formed such that the tooth surface or the groove surface forms an involute curve. Thus, in the belt-type continuously variable transmission 9, the movable sheave 38 can be moved in the axial direction with respect to the primary shaft (rotary shaft) SP by the spline 38s and the spline groove SPg, while the circumferential direction of the primary shaft SP is changed. Is immovable.
[0034]
Further, the belt-type continuously variable transmission 9 includes an annular partition member (piston) 70. As can be seen from FIG. 2, the partition member 70 includes a base end portion 71 extending in the radial direction of the primary shaft SP, an intermediate portion 72 extending substantially parallel to the primary shaft SP from the base end portion 71, and a movable sheave from the intermediate portion 72. An outer peripheral portion 73 extends in the radial direction of the primary shaft SP along the back surface 38a of the main shaft 38.
[0035]
A small-diameter portion at the distal end (the end on the bearing 32 side) of the primary shaft SP is press-fitted into a hole formed in the base end portion 71 of the partition wall member 70. It is fixed to the shaft SP. The base end 71 of the partition member 70 is rotatably supported by a bearing 32 fixed to the transaxle rear cover 6 by a support member 81 or the like. Thus, in the belt-type continuously variable transmission 9, the primary shaft SP is rotatably supported by the bearing 32 via the partition member 70 (the base end 71).
[0036]
A seal member 74 is arranged on the outer edge of the outer peripheral portion 73 of the partition member 70 so as to be in sliding contact with the inner peripheral surface of the cylindrical portion 38b formed on the outer periphery of the movable sheave 38. As a result, the oil chamber 40a of the hydraulic actuator 40 is defined by the rear surface 38a of the movable sheave 38, the cylindrical portion 38b, and the partition member 70. By controlling the oil pressure in the oil chamber 40a, the movable sheave 38 is moved with respect to the fixed sheave 37 to change the winding radius of the belt B, so that a desired gear ratio can be obtained.
[0037]
Here, as described above, the belt-type continuously variable transmission 9 uses a very simple spline (involute spline) to allow the movable sheave 38 to move in the axial direction with respect to the primary shaft SP, while allowing the movement with respect to the primary shaft SP. The rotation of the movable sheave 38 is restricted. In this case, in order to stabilize the operation of the movable sheave 38, it is necessary to provide the movable sheave 38 with a sliding portion that comes into contact with the primary shaft SP or the like. Further, when forming the spline in the movable sheave 38, it is necessary to prevent the manufacturing cost from unnecessarily increasing.
[0038]
In view of these points, in the belt-type continuously variable transmission 9, with respect to the movable sheave 38, the first sliding portion 38c and the second sliding portion are provided on both sides of the spline 38s in the axial direction of the primary shaft SP. 38d. Of the two sliding portions 38c and 38d of the movable sheave 38, the first sliding portion 38c is on the fixed sheave 37 side in the axial direction of the primary shaft SP with respect to the spline 38s, and on the inner peripheral surface of the movable sheave 38. And is in contact with the outer peripheral surface of the primary shaft SP. On the other hand, the second sliding portion 38d is provided on the opposite side (the rear cover 6 side) of the first sliding portion 38d across the spline 38s and on the outer peripheral surface of the movable sheave 38. Then, as shown in FIG. 2, the second sliding portion 38 contacts not the primary shaft SP but the inner peripheral surface of the intermediate portion 72 of the partition member 70.
[0039]
As described above, in the belt-type continuously variable transmission 9, the second sliding portion 38d is provided on the outer peripheral surface of the movable sheave 38, and is configured to be in contact with the partition member 70 which is a member other than the primary shaft SP. I have. That is, with such a configuration, it is not necessary to bring the region located inside the second sliding portion 38d in FIG. 2 on the inner peripheral surface of the movable sheave 38 into contact with the outer peripheral surface of the primary shaft SP. This makes it possible to make the inner diameter of a region located inside the second sliding portion 38d of the inner peripheral surface of the movable sheave 38 larger than the outer diameter of the primary shaft SP.
[0040]
As a result, when the spline 38s is formed on the movable sheave 38, the movement of the tool is not hindered by the second sliding portion 38d, so that the broach is moved from one side of the sliding portions 38c and 38d to the other side. The spline 38s can be formed by processing while moving a tool such as. That is, it is not necessary to use a slotter or the like for forming the spline 38s, and the spline 38s can be formed on the movable sheave 38 very easily at low cost in a short time. In addition, in the belt-type continuously variable transmission 9, since the sliding portions 38c and 38d are secured on both sides of the spline 38s in the axial direction of the primary shaft SP, the operation of the movable sheave 38 with respect to the primary shaft SP is extremely excellent. Can be stabilized.
[0041]
Further, in the above-described continuously variable transmission 9, as can be seen from FIG. 2, of the inner peripheral surface of the movable sheave 38, the region located inside the second sliding portion 38 d and the outer peripheral surface of the primary shaft SP Between them, a cylindrical gap 82 can be formed. The gap 82 is always in communication with the oil chamber 40a via at least one oil passage 38e formed at the end of the movable sheave 38 including the second sliding portion 38d.
[0042]
In such a configuration, if one radial oil passage SPb is provided for the primary shaft SP, the oil passage SPa inside the primary shaft SP connected to an external hydraulic device (not shown) is provided. Therefore, the working oil can always be smoothly supplied to the gap 82. Thus, regardless of the position of the movable sheave 38 in the axial direction of the primary shaft SP, a desired amount of operation is performed from the gap 82 into the oil chamber 40a through the oil passage 38e of the movable sheave 38 without causing a so-called oil pool. It becomes possible to supply oil. As a result, in the continuously variable transmission 9, it is possible to control the hydraulic pressure applied to the movable sheave 38 with good responsiveness.
[0043]
In the above-described first embodiment, the movable sheave 38 can be moved in the axial direction with respect to the primary shaft SP using the involute spline, but cannot be moved in the circumferential direction of the primary shaft SP. It is not limited. That is, instead of the involute spline, a ball spline or a spline that does not use a ball other than the involute spline may be used.
[0044]
[Second embodiment]
Hereinafter, a belt-type continuously variable transmission according to a second embodiment of the present invention will be described with reference to FIG. Note that the same elements as those described in relation to the above-described first embodiment are denoted by the same reference numerals, and redundant description will be omitted.
[0045]
In the belt-type continuously variable transmission 9A shown in FIG. 4, the partition member 70A fixed to the primary shaft SP so as to define the oil chamber 40a together with the movable sheave 38 moves the cylindrical portion 75 covering the outer periphery of the primary shaft SP. Have. In the present embodiment, the cylindrical portion 75 extends in the axial direction of the primary shaft SP from the base end portion 71 of the partition member 70A toward the fixed sheave 37. The movable sheave 38 of the continuously variable transmission 9A also has a first sliding portion 38c and a second sliding portion 38d on both sides of the spline 38s in the axial direction of the primary shaft SP. In this case, the first and second sliding portions 38c and 38d are both provided on the inner peripheral surface of the movable sheave 38, but the first sliding portion 38c on the fixed sheave 37 side is While the second sliding portion 38d on the rear cover 6 side contacts the outer peripheral surface, the second sliding portion 38d contacts the outer peripheral surface of the cylindrical portion 75 of the partition member 70A.
[0046]
As described above, by configuring the second sliding portion 38d to be in contact with the cylindrical portion 75 of the partition member 70A fixed to the primary shaft SP, the inner radius of the second sliding portion 38d can be reduced. Can be made larger than the outer diameter of the cylindrical portion 75 by the thickness of the cylindrical portion 75. As a result, when the spline 38s is formed on the movable sheave 38, the movement of the tool is not hindered by the second sliding portion 38d, so that the broach is moved from one side of the sliding portions 38c and 38d to the other side. The spline 38s can be formed by processing while moving a tool such as. That is, it is not necessary to use a slotter or the like for forming the spline 38s, and the spline 38s can be formed on the movable sheave 38 very easily at low cost in a short time.
[0047]
Further, by providing the cylindrical portion 75 on the partition member 70A, the press-fit area between the partition member 70A and the primary shaft SP can be increased by the inner peripheral area of the cylindrical portion 75. This makes it possible to increase the holding force of the partition member 70A on the primary shaft SP while lowering the surface pressure, thereby reducing the load on the lock nut 80. As a result, the axial length of the lock nut 80 can be reduced, so that the continuously variable transmission 9A can be made more compact.
[0048]
Also, in the belt-type continuously variable transmission 9A, since the sliding portions 38c and 38d are secured on both sides of the spline 38s in the axial direction of the primary shaft SP, the operation of the movable sheave 38 with respect to the primary shaft SP is extremely excellent. Can be stabilized. Further, in the case of the present embodiment, it is preferable that at least two radial oil passages SPb and SPc that can communicate with the oil passage 38e of the movable sheave 38 are formed in the primary shaft SP. Thus, regardless of the position of the movable sheave 38 in the axial direction of the primary shaft SP, a desired amount of hydraulic oil can be supplied into the oil chamber 40a without causing a so-called oil pool.
[0049]
In addition, from the viewpoint of improving the retention of the partition member 70A, the cylindrical portion 75 is preferably integrated with the partition member 70A, but is not limited thereto. That is, as shown in FIG. 5, the cylindrical member 85 separate from both the partition wall member 70 and the primary shaft SP is positioned with respect to the primary shaft SP, and the second sliding portion 38d of the movable sheave 38 is moved. You may make it contact the outer peripheral surface of the cylindrical member 85. In the above-described second embodiment, the movable sheave 38 can be moved in the axial direction with respect to the primary shaft SP by using the involute spline, but cannot be moved in the circumferential direction of the primary shaft SP. It is not limited to. That is, instead of the involute spline, a ball spline or a spline that does not use a ball other than the involute spline may be used.
[0050]
[Third embodiment]
Hereinafter, a belt-type continuously variable transmission according to a third embodiment of the present invention will be described with reference to FIG. The same elements as those described in connection with the above-described first embodiment and the like are denoted by the same reference numerals, and redundant description will be omitted.
[0051]
The movable sheave 38 of the belt-type continuously variable transmission 9B shown in FIG. 6 also has a first sliding portion 38c and a second sliding portion 38d on both sides of the spline 38s in the axial direction of the primary shaft SP. Of these sliding portions 38c and 38d, the second sliding portion 38d is provided at the outermost end 38g on the opposite side of the pulley groove 39 in the axial direction of the movable sheave 38. In this case, the first and second sliding portions 38c and 38d are both provided on the inner peripheral surface of the movable sheave 38 and contact the outer peripheral surface of the primary shaft SP, but the second sliding member on the rear cover 6 side. A plurality of grooves 38f extending parallel to each spline 38s are formed in the moving part 38d. In the present embodiment, it is preferable to use a spline that does not use a ball, such as an involute spline, as the spline.
[0052]
Under such a configuration, by processing from one side of the sliding portions 38c and 38d to the other side with a tool such as a broach, each spline 38s is formed together with the groove 38f of the second sliding portion 38d. It can be formed simultaneously with the movable sheave 38. That is, even with the configuration of the present embodiment, it is not necessary to use a slotter or the like for forming the spline 38s, and the spline 38s can be formed on the movable sheave 38 very easily at a low cost and in a short time. It becomes possible. Also in the belt-type continuously variable transmission 9B, the sliding portions 38c and 38d are secured on both sides of the spline 38s in the axial direction of the primary shaft SP, and the sliding portion 38d (sliding surface) is the extreme end of the movable sheave 38. Since the portion is effectively provided up to the portion 38g, the operation of the movable sheave 38 with respect to the primary shaft SP can be stabilized very well.
[0053]
Also in the continuously variable transmission 9B of the present embodiment, as can be seen from FIG. 6, the inner peripheral surface of the movable sheave 38 has a region near the second sliding portion 38d and an outer peripheral surface of the primary shaft SP. Between them, a cylindrical gap 82 communicating with each groove 38f of the second sliding portion 38d can be formed. Also in this case, if at least one radial oil passage SPb is provided for the primary shaft SP, a gap is formed between the oil passage SPa inside the primary shaft SP and the oil passage SPa connected to an external hydraulic device (not shown). Hydraulic oil can always be smoothly supplied to 82. Thus, regardless of the position of the movable sheave 38 in the axial direction of the primary shaft SP, a desired amount of operation is performed from the gap 82 into the oil chamber 40a through the oil passage 38e of the movable sheave 38 without causing a so-called oil pool. It becomes possible to supply oil. As a result, also in the continuously variable transmission 9B, it is possible to control the hydraulic pressure applied to the movable sheave 38 with good responsiveness.
[0054]
In each of the above embodiments, the present invention has been described as being applied to the primary pulley and the primary shaft, but the present invention is not limited to this, and the present invention may be applied to the secondary pulley and the secondary shaft. It goes without saying that it can be applied.
[0055]
【The invention's effect】
As described above, according to the present invention, a spline can be easily formed on a movable sheave, and the operation of the movable sheave of a continuously variable transmission can be favorably stabilized.
[Brief description of the drawings]
FIG. 1 is a schematic configuration diagram showing a vehicle to which a continuously variable transmission according to a first embodiment of the present invention is applied.
FIG. 2 is an enlarged sectional view of a main part showing a first embodiment of a continuously variable transmission according to the present invention.
FIG. 3 is a cross-sectional view illustrating the continuously variable transmission shown in FIG.
FIG. 4 is an enlarged sectional view showing a main part of a continuously variable transmission according to a second embodiment of the present invention.
FIG. 5 is an enlarged sectional view of a main part showing a modification of the continuously variable transmission shown in FIG.
FIG. 6 is an enlarged sectional view showing a main part of a continuously variable transmission according to a third embodiment of the present invention.
[Explanation of symbols]
1 vehicle
2 Engine
3 Transaxle
7 Torque converter
8. Forward / backward switching mechanism
9,9A, 9B belt type continuously variable transmission
10 Final reducer
19 Damper mechanism
20 Lock-up clutch
21 Oil pump
25 planetary gear mechanism
35 Primary pulley
36 Secondary pulley
37, 41 Fixed sheave
38, 42 Movable sheave
38s spline
38a back
38b tubular part
38c First sliding part
38d second sliding part
38e oilway
38f groove
38g extreme end
39,44 Pulley groove
40,45 hydraulic actuator
40a Oil chamber
70, 70A Partition member
71 Base end
72 Middle part
73 Outer circumference
74 Sealing member
75 cylindrical part
80 Lock nut
81 Supporting member
82 gap
85 cylindrical member
B belt
SP primary shaft
SPa oilway
SPb, SPc radial oil passage
SPg Spline groove
SS secondary shaft

Claims (5)

Including a movable sheave and a fixed sheave arranged on the outer periphery of the rotating shaft, and a belt wound around the movable sheave and the fixed sheave, moving the movable sheave with respect to the fixed sheave, the winding radius of the belt In a belt-type continuously variable transmission that can obtain a desired gear ratio by changing
The movable sheave,
A spline for restricting rotation of the movable sheave with respect to the rotating shaft, while allowing axial movement of the movable sheave with respect to the rotating shaft,
A first sliding portion that is provided on an inner peripheral portion of the movable sheave and laterally of the spline in the axial direction of the rotating shaft, and that is in contact with an outer peripheral surface of the rotating shaft;
A second sliding portion that is provided on the opposite side of the first sliding portion with respect to the spline and on an outer peripheral portion of the movable sheave, and is in contact with a member other than the rotating shaft. Belt type continuously variable transmission. The belt-type continuously variable transmission according to claim 1, wherein the member other than the rotation shaft is a partition member that defines an oil chamber for applying a hydraulic pressure to the movable sheave. Including a movable sheave and a fixed sheave arranged on the outer periphery of the rotating shaft, and a belt wound around the movable sheave and the fixed sheave, moving the movable sheave with respect to the fixed sheave, the winding radius of the belt In a belt-type continuously variable transmission that can obtain a desired gear ratio by changing
Having a cylindrical portion that covers the outer periphery of the rotating shaft, and including a member fixed to the rotating shaft,
The movable sheave,
A spline for restricting rotation of the movable sheave with respect to the rotating shaft, while allowing axial movement of the movable sheave with respect to the rotating shaft,
A first sliding portion that is provided on an inner peripheral portion of the movable sheave and laterally of the spline in the axial direction of the rotating shaft, and that is in contact with an outer peripheral surface of the rotating shaft;
A second side, which is provided on the opposite side of the first sliding portion with respect to the spline and on an inner peripheral portion of the movable sheave and in contact with an outer peripheral surface of the cylindrical portion of a member fixed to the rotating shaft; A belt-type continuously variable transmission, comprising: The belt-type continuously variable transmission according to claim 3, wherein the member fixed to the rotating shaft is a partition member that defines an oil chamber for applying a hydraulic pressure to the movable sheave. Including a movable sheave and a fixed sheave arranged on the outer periphery of the rotating shaft, and a belt wound around the movable sheave and the fixed sheave, moving the movable sheave with respect to the fixed sheave, the winding radius of the belt In a belt-type continuously variable transmission that can obtain a desired gear ratio by changing
The movable sheave,
A spline for restricting rotation of the movable sheave with respect to the rotating shaft, while allowing axial movement of the movable sheave with respect to the rotating shaft,
A first sliding portion that is provided on an inner peripheral portion of the movable sheave and laterally of the spline in the axial direction of the rotating shaft, and that is in contact with an outer peripheral surface of the rotating shaft;
It is provided on the inner peripheral portion of the movable sheave and the axially outermost portion of the movable sheave on the opposite side of the first sliding portion with respect to the spline, and is in contact with the outer peripheral surface of the rotating shaft. A second sliding portion, wherein a plurality of grooves extending parallel to the spline are formed in the second sliding portion.

Images