JP5206232B2 - Belt type continuously variable transmission - Google Patents

Description

  The present invention relates to a belt-type continuously variable transmission used as, for example, an automobile transmission. In particular, the present invention relates to an improvement in a member for performing position adjustment between components constituting a belt type continuously variable transmission.

  2. Description of the Related Art Conventionally, a belt-type continuously variable transmission (belt-type CVT: Continuously Variable Transmission) is known as a transmission mounted on the output side of an automobile engine. This belt-type continuously variable transmission includes two shafts (primary shaft and secondary shaft) arranged in parallel to each other, as disclosed in, for example, Patent Document 1 and Patent Document 2 below, and each shaft individually. A primary pulley and a secondary pulley. Both the primary pulley and the secondary pulley have a combination of a fixed sheave and a movable sheave. Specifically, the fixed sheave is provided integrally with each shaft, whereas the movable sheave is provided so as to be movable along the axial direction of the shaft, and can be brought into and out of contact with the fixed sheave. Yes.

  A V-shaped groove is formed between the fixed sheave and the movable sheave of each pulley. A V belt is wound around the V groove of the primary pulley and the V groove of the secondary pulley. A hydraulic chamber for generating a clamping pressure by both sheaves for the V-belt is provided separately for each pulley.

  In such a belt type continuously variable transmission, by individually controlling the hydraulic pressure of each hydraulic chamber, the movable sheave of each pulley moves forward and backward toward the fixed sheave, and the groove width of the V groove of each pulley is changed. Is done. Thereby, the winding position of the V-belt in the radial direction of each pulley, in other words, the winding radius of the V-belt of each pulley is changed, and the gear ratio in the belt-type continuously variable transmission is changed steplessly. It has become.

  FIG. 5 is a cross-sectional view showing a configuration on the primary pulley side in a conventional general belt type continuously variable transmission. In FIG. 5, the state in which the winding radius of the V belt b with respect to the primary pulley a is reduced is shown in the upper half, and the state in which the winding radius is increased is shown in the lower half.

  The primary pulley a includes a fixed sheave d formed integrally with the primary shaft c, and a movable sheave e disposed so as to be movable forward and backward with respect to the fixed sheave d. The movable sheave e is continuously formed from the inner cylindrical portion e1 that slides along the outer peripheral surface of the primary shaft c and the end portion (end portion on the fixed sheave d side) of the inner cylindrical portion e1 toward the outer peripheral side. A radial direction part e2, and a substantially cylindrical outer cylinder part e3 which is continuously formed at the outer peripheral end of the radial direction part e2 and extends in a direction opposite to the side where the fixed sheave d is disposed. ing.

  Further, a cylinder member f is disposed on the back side of the movable sheave e. The cylinder member f is directed to the outside so as to be continuous with the inner radial direction portion f1 constituting the inner peripheral portion thereof and the inner radial direction portion f1 and facing the back surface of the radial direction portion e2 of the movable sheave e. The outer radial direction part f2 extended and the cylindrical part f3 which is continuously formed on the outer peripheral side of the outer radial direction part f2 and is located on the outer peripheral side of the outer cylindrical part e3 of the movable sheave e. . And the step part c1 is formed in the front-end | tip part vicinity position of the said primary shaft c, The said inner side radial direction part f1 of the cylinder member f is between this step part c1 and the inner race g1 of the bearing g, It is fixed to the primary shaft c by a lock nut h that is clamped together with a cylinder seat j to be described later and is tightened to the outer periphery of the primary shaft c.

  The cylinder seat j is made of an annular plate material, and is interposed between the inner radial direction part f1 of the cylinder member f and the step part c1 of the primary shaft c, and the outer diameter dimension thereof is the outer diameter of the primary shaft c. It is set larger than the dimension. For this reason, when the movable sheave e moves to the retracted position farthest from the fixed sheave d, the retracted position is defined by the rear end surface of the movable sheave e coming into contact with the cylinder seat j. (See the state of the upper half of FIG. 5). That is, the cylinder seat j functions as a stopper.

  Further, the position of the movable sheave e near the tip of the outer cylindrical portion e3 is in contact with the inner surface of the cylindrical portion f3 of the cylinder member f via the seal ring e4, and the seal ring e4 and the inner surface of the cylindrical portion f3 A sealing surface is formed between the two. As a result, a space surrounded by the movable sheave e and the cylinder member f is formed as a control hydraulic chamber i constituting the hydraulic actuator of the primary pulley a, and the hydraulic pressure in the control hydraulic chamber i is controlled (the amount of supplied oil is reduced). Control), the moving position of the movable sheave e with respect to the fixed sheave d is changed.

A shim n is interposed between the outer race g2 of the bearing g and the case (Rr case) m. The shim n defines the position (axial center position) of the outer race g2 of the bearing g with respect to the case m, so that the axial position of the fixed sheave d via the bearing g, the cylinder member f, and the primary shaft c. It prescribes. That is, when assembling the belt-type continuously variable transmission, a plurality of types of shims n having different thicknesses are prepared in advance, and by selecting and installing shims with appropriate thicknesses, the axial direction of the fixed sheave d The position of is being obtained appropriately. As a result, the V-belt b wound between the primary pulley a and the secondary pulley is wound so as to extend in a direction orthogonal to the axial extension directions of the primary shaft c and the secondary shaft. Since the side surface of the V belt b comes into contact with the sheaves d and e uniformly, the durability of the V belt b can be improved.
JP 2005-249162 A Japanese Utility Model Publication No. 6-32751

  By the way, in a conventional belt-type continuously variable transmission, a belt-type continuously variable transmission of a different type is often employed for each displacement of an engine connected thereto. For example, a belt-type continuously variable transmission with a large size and a relatively small maximum transmission ratio (maximum reduction ratio) is adopted for a large displacement engine, and conversely, a small and maximum transmission ratio for a small displacement engine. A belt type continuously variable transmission is used. In this case, it is necessary to prepare the cylinder seat j and shim n for each belt type continuously variable transmission type. As described above, as the shim n, it is necessary to prepare a plurality of types having different thicknesses for each type of belt-type continuously variable transmission.

  For example, when five types of belt type continuously variable transmissions are produced, it is necessary to prepare a cylinder seat j corresponding to each type. That is, as the cylinder seat j, it is necessary to manufacture five types according to each model of the belt type continuously variable transmission. Further, as described above, as the shim n, it is necessary to prepare a plurality of types for each model. For example, when producing five types of belt-type continuously variable transmissions as described above, when it is necessary to prepare ten types of shims n having different thicknesses for each belt-type continuously variable transmission in advance, There was a possibility that 50 kinds of shims n had to be manufactured.

  In this way, many types of cylinder seats j and shims n (in the above case, 5 types for cylinder seats j and 50 types for shims n, a total of 55 types) are manufactured in advance, and these cylinder seats j and shims n Must be managed individually, and the management is complicated, and the production cost of the belt-type continuously variable transmission has increased.

  The present invention has been made in view of the above points, and an object of the present invention is to eliminate a complicated part management and reduce a production cost. Is to provide.

-Principle of solving the problem-
The solution principle of the present invention taken to achieve the above object is to define a function as a shim for positioning a shaft member such as a primary shaft in the axial direction and a last retracted position of the movable sheave. By combining the function as a stopper with a single member, individual manufacturing and individual management of the conventional shim and cylinder seat are not required.

-Solution-
Specifically, according to the present invention, a driving pulley having a fixed sheave and a movable sheave is provided on one of a pair of shaft members parallel to each other, and a driven pulley having a fixed sheave and a movable sheave on the other is provided. The belt means is spanned between these pulleys so that the rotational force of the driving pulley can be transmitted to the driven pulley via the belt means, and each movable sheave is fixed to the fixed sheave. The belt-type continuously variable transmission is assumed to be capable of changing the gear ratio by changing the winding position of the belt means in the radial direction of each pulley by moving the pulley forward and backward. An adjustment member is attached to at least one of the shaft members for the belt type continuously variable transmission. A shim function part that defines a position in the axial direction of the shaft member by contacting the adjusting member with a contact surface extending in a substantially radial direction on the shaft member, and a direction in which the movable sheave moves away from the fixed sheave. A stopper function part is provided for defining the last retracted position of the movable sheave by contacting the movable sheave when moved. Further, the adjustment member is mounted on the shaft member by selecting one from a plurality of types having different thickness dimensions in the axial direction in the shim function portion and in the axial direction in the stopper function portion. Has been.
More specifically, the adjustment member is attached to a shaft member provided with a driving pulley, and the internal combustion engine connected from among a plurality of types of adjustment members having different thickness dimensions of the stopper function portion. It is assumed that it has been selected according to the model.

  With this specific matter, the position of the shaft member in the axial center direction is defined by the shim function portion of the adjustment member. That is, by appropriately obtaining the position of the shaft member in the axial center direction, the relative positions of the fixed sheaves of the driving pulley and the driven pulley can be appropriately obtained. Since the shaft member extends in a direction orthogonal to the axial extension direction of each shaft member, the durability of the belt can be ensured. Further, when the movable sheave moves to the retracted position farthest from the fixed sheave, the movable sheave contacts the stopper function portion of the adjustment member. That is, the movable sheave is restricted from moving backward from the contact position. Therefore, this adjusting member defines the shim function for adjusting the position of the shaft member in the axial direction, the function as a stopper that contacts the movable sheave, and the gear ratio (for example, the maximum gear ratio of the belt-type continuously variable transmission). The conventional shim (single part having only the shim function) can be abolished. As described above, in the present solution, the shim function, the stopper function, and the gear ratio defining function can be used as one member. Conventionally, it has been necessary to individually manufacture and manage the shim that exhibits the shim function and the cylinder seat that exhibits the stopper function, but this solution eliminates the necessity and complicates parts management. This can be eliminated, and the production cost can be reduced.

In addition, the shim function, the stopper function, and the gear ratio defining function are effectively exhibited, ensuring the durability of the belt by the shim function, defining the last retracted position of the movable sheave by the stopper function, and the gear ratio by the gear ratio defining function ( (Maximum gear ratio) can be properly defined. In particular, since this adjustment member has the gear ratio defining function, when applied to a shaft member (primary shaft) provided with a drive pulley as described above, it is a belt-type continuously variable transmission having the same configuration. Even in such a case, it is possible to construct transmissions with different maximum speed ratios by changing the adjustment member to be applied. For example, for a belt-type continuously variable transmission connected to a small displacement engine, an adjustment member with a small thickness of the stopper function portion is applied to increase the maximum gear ratio, so that the transmission torque to the drive wheels is increased. Make it big. As a result, even when a small displacement engine is installed, it is possible to sufficiently exhibit the start acceleration performance of the vehicle. Conversely, for belt-type continuously variable transmissions connected to a large displacement engine, an adjustment member with a large stopper function is used to reduce the maximum gear ratio and keep the engine speed low. . As a result, it is possible to improve the fuel consumption rate by restricting the maximum gear ratio while ensuring high running performance with a relatively large torque output from the large displacement engine.

  As described above, even in the belt-type continuously variable transmission having the same configuration, by appropriately selecting an adjustment member to be applied (an adjustment member having a different thickness dimension of the stopper function portion), a speed change according to the engine displacement is performed. It can be configured as a belt type continuously variable transmission having characteristics. That is, while connecting the belt-type continuously variable transmission of the same configuration to each of the various engines (engines having different displacements), by appropriately selecting the adjusting member, the shift characteristics of the belt-type continuously variable transmission can be The characteristics can be adjusted according to the engine. For this reason, the versatility of one type of belt-type continuously variable transmission can be greatly expanded, it is not necessary to individually design a belt-type continuously variable transmission for each type of engine, and for each type of engine There is no need to separately manufacture the components of the belt-type continuously variable transmission, and the cost can be greatly reduced.

  Specific examples of the configuration of the shaft member and the adjustment member include the following. First, the shaft member is connected to a large-diameter portion where the movable sheave moves forward and backward, a small-diameter portion formed on the movable sheave retracting side from the large-diameter portion, and the large-diameter portion and the small-diameter portion. The contact surface extending in a substantially radial direction is formed. Further, the shim function portion of the adjustment member is formed of an annular plate member having an inner diameter dimension that substantially matches the outer diameter dimension of the small diameter portion. Further, the stopper function portion of the adjustment member is formed of an annular member that is continuously formed on the outer peripheral side of the shim function portion and has an inner diameter dimension that substantially matches the outer diameter dimension of the large diameter section. The position of the shaft member in the axial direction is defined by the shim function portion of the adjustment member coming into contact with the contact surface, and the stopper function portion is located on the outer peripheral side of the shim function portion. The last retracted position of the movable sheave is defined by being located on the outer peripheral side of the.

  Further, a bearing for rotatably supporting the shaft member is disposed at one end portion of the shaft member, and the fastening force is obtained by attaching a lock nut to the male screw portion formed at the one end portion of the shaft member. However, it is set as the structure which presses the said shim function part to the said contact surface of a shaft member via the inner race of a bearing.

  With the configuration described above, the shape of the adjustment member can be a shape along the small diameter portion, the contact surface, and the large diameter portion of the shaft member, and the adjustment member can be stably assembled to the shaft member. . For this reason, the shim function, stopper function, and gear ratio defining function described above can be stably obtained over a long period of time, and the reliability of the belt type continuously variable transmission can be improved.

  In the present invention, the adjustment member has both a function as a shim for positioning the shaft member of the belt type continuously variable transmission in the axial direction and a function as a stopper for defining the last retracted position of the movable sheave. I try to let them. Thereby, the conventional shim can be abolished, and individual manufacturing and individual management of the shim and the cylinder seat are not necessary.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the present embodiment, a case where the present invention is applied to a belt type continuously variable transmission for an automobile will be described. A belt type continuously variable transmission mounted on an FF (front engine / front drive) vehicle will be described as an example. 1 and 2, the side where the engine (internal combustion engine) is disposed (the right side in the figure) is the Fr (front) direction side, and the opposite side (the left side in the figure) is the Rr (rear) direction side. (In fact, it is the left-right direction of the vehicle).

(Overall structure of transaxle)
First, the overall configuration of the transaxle on which the belt type continuously variable transmission 30 is mounted will be described.

  FIG. 1 is a skeleton diagram of a transaxle. As shown in FIG. 1, the rotational power of the crankshaft 1 a of the engine 1 is transmitted to the wheels 3 via a power transmission system 2. The engine 1 and the power transmission system 2 are controlled by an engine control unit (ECU) 4.

  The power transmission system 2 includes a torque converter 10 as a clutch, a forward / reverse switching mechanism 20, a belt-type continuously variable transmission 30, a speed reduction mechanism 40, and a differential device 50. Hereinafter, these configurations will be described.

  The torque converter 10 functions as a torque amplifier when the rotational speed difference between the pump impeller 13a and the turbine runner 13b is large, and functions as a fluid coupling when the rotational speed difference between the two becomes small.

  As the operation of the torque converter 10, the pump impeller 13 a rotates through the drive plate 11 and the front cover 12 as the crankshaft 1 a of the engine 1 rotates, and the turbine is driven by the flow of hydraulic fluid supplied from the oil pump 14. The runner 13b starts to rotate so as to be dragged. When the rotational speed difference between the pump impeller 13a and the turbine runner 13b is large, the stator 13c converts the flow of hydraulic fluid into a direction that assists the rotation of the pump impeller 13a.

  When the vehicle speed reaches a predetermined speed after the vehicle starts, the lock-up clutch 15 is operated so that the power transmitted from the engine 1 to the front cover 12 is mechanically and directly transmitted to the input shaft 16. Become. In addition, fluctuations in torque transmitted from the front cover 12 to the input shaft 16 are absorbed by the damper mechanism 17.

  The forward / reverse switching mechanism 20 includes a double pinion planetary gear mechanism 21, a forward clutch 22, and a reverse brake 23.

  The sun gear 21a of the planetary gear mechanism 21 is connected to the input shaft 16 and the carrier 21b of the planetary gear mechanism 21 is connected to the primary shaft (drive side shaft) 31 of the belt-type continuously variable transmission 30, respectively. The power transmission path is changed by controlling the reverse brake 23, and the rotational force from the input shaft 16 is converted into forward rotational power (rotational power in the forward rotational direction) and backward rotational power (rotational power in the reverse rotational direction). Switch between.

  The belt-type continuously variable transmission 30 continuously changes the rotation of a primary shaft (shaft member) 31 that is an input shaft (drive shaft) and transmits the rotation to a secondary shaft 32 that is an output shaft (driven shaft). is there. A V belt (belt means) 33 is wound around a primary pulley (driving pulley) 34 of the primary shaft 31 and a secondary pulley (driven pulley) 35 of the secondary shaft 32. Both the primary pulley 34 and the secondary pulley 35 are configured by combining fixed sheaves 34a and 35a and movable sheaves 34b and 35b. The primary shaft 31 and the secondary shaft 32 are made of metal such as iron, for example. The V-belt 33 has a large number of metal pieces and a plurality of steel rings.

  The primary shaft 31 is supported by a partition wall portion 81a and an Rr case 82 that are provided integrally with the Fr case 81 via bearings (bearings) 61 and 62 so as to be substantially coaxial with the input shaft 16 of the torque converter 10. ing. The secondary shaft 32 is supported by a partition wall portion 81 b and an Rr case 82 that are provided integrally with the Fr case 81 via bearings 63 and 64 so as to be parallel to the primary shaft 31.

  The primary pulley 34 includes a fixed sheave 34a integrally formed on the outer periphery of the primary shaft 31, and a movable sheave 34b mounted on the outer periphery of the primary shaft 31 so as to be axially displaceable. The fixed sheave 34a and the movable sheave 34 The V-belt 33 is clamped by 34b. Then, by driving the movable sheave 34b by the hydraulic actuator 36, the V groove width between the sheaves 34a and 34b is changed. Thereby, the winding position of the V belt 33 in the radial direction of the primary pulley 34, in other words, the winding radius of the V belt 33 of the primary pulley 34 is changed.

  The secondary pulley 35 includes a fixed sheave 35a that is integrally formed on the outer periphery of the secondary shaft 32 and a movable sheave 35b that is mounted on the outer periphery of the secondary shaft 32 so as to be axially displaceable. The fixed sheave 35a and the movable sheave The V belt 33 is clamped by 35b. Then, by driving the movable sheave 35b with the hydraulic actuator 37, the V groove width between the sheaves 35a and 35b is changed. Thereby, the winding position of the V belt 33 in the radial direction of the secondary pulley 35, in other words, the winding radius of the V belt 33 of the secondary pulley 35 is changed. A parking gear 38 is provided on the Rr direction side of the secondary pulley 35 of the secondary shaft 32.

  As described above, in the belt type continuously variable transmission 30, the movable sheaves 34b and 35b of the pulleys 34 and 35 are moved forward and backward with respect to the fixed sheaves 34a and 35a by the hydraulic actuators 36 and 37, respectively. By adjusting the V groove width, the winding position of the V belt 33 in the radial direction of the pulleys 34 and 35 is changed, and the gear ratio by the belt type continuously variable transmission 30 is changed.

  The speed reduction mechanism 40 has two counter driven gears 41 and 42 that mesh with each other and a final drive gear 43. The first counter driven gear 41 is fixed to a shaft 44 connected to the secondary shaft 32 of the belt type continuously variable transmission 30. The second counter driven gear 42 and the final drive gear 43 are respectively fixed to an intermediate shaft 45 disposed substantially parallel to the secondary shaft 32 so as to be separated from each other in the axial direction. The shaft 44 is supported via bearings 65 and 66, and the intermediate shaft 45 is supported via bearings 67 and 68, respectively.

  The differential device (final speed reduction device) 50 distributes and transmits the rotational power transmitted from the speed reduction mechanism 40 to the wheels 3 connected to the pair of left and right axle shafts 51 and 52 at an appropriate ratio. The differential case 53 is disposed.

(Specific configuration around the primary pulley 34)
Next, a specific configuration of the primary pulley 34 and its peripheral part in the belt type continuously variable transmission 30 will be described with reference to FIG.

  FIG. 2 is a cross-sectional view showing a specific configuration of the primary pulley 34 and its peripheral portion of the belt type continuously variable transmission 30. The upper half of FIG. 2 shows a state in which the winding radius of the V belt 33 with respect to the primary pulley 34 is reduced, and the lower half shows a state in which the winding radius of the V belt 33 with respect to the primary pulley 34 is increased. .

  The primary shaft 31 is supported by a partition wall portion 81a and an Rr case 82 that are integrally provided in the Fr case 81 via an Fr bearing 61 on the Fr direction side and an Rr bearing 62 in the Rr direction. Hereinafter, the partition wall portion 81 a and the Rr case 82 of the Fr case 81 that supports the primary shaft 31 are referred to as a transmission case 80. The transmission case 80 is made of a metal such as an aluminum alloy, for example.

  The primary pulley 34 is provided on the primary shaft 31 and is disposed between the Fr bearing 61 and the Rr bearing 62. In other words, the Fr bearing 61 and the Rr bearing 62 are respectively arranged on both sides of the primary pulley 34 on the primary shaft 31. Thereby, the primary shaft 31 and the primary pulley 34 provided thereon can be rotated about the axis A <b> 1 with respect to the transmission case 80.

  The primary shaft 31 has a distal end portion 31a to which the Fr bearing 61 is mounted on the Fr direction side of the fixed sheave 34a, an intermediate portion 31b in which the fixed sheave 34a is formed and the movable sheave 34b is mounted, and more than the movable sheave 34b. On the Rr direction side, a cylinder member 75, an adjustment member 90, and a rear end portion 31c to which the Rr bearing 62 is mounted are provided. A step 31d is formed at the boundary between the intermediate portion 31b and the rear end portion 31c. A lock nut 31f is fastened to the Rr direction side of the Rr bearing 62 of the rear end portion 31c. By tightening the lock nut 31f, the movable sheave 34b, the adjustment member 90, the cylinder member 75, and the Rr bearing 62 provided on the primary shaft 31 are assembled together.

  Further, the input shaft 16 of the torque converter 10 is spline-fitted to the inner peripheral side of the tip 31a of the primary shaft 31. An oil passage 71 extending in the axial direction is formed inside the primary shaft 31. The oil passage 71 is open at the rear end surface of the primary shaft 31, and hydraulic oil from a hydraulic circuit (not shown) is supplied to the oil passage 71 via a hydraulic actuator 36. Oil passages 73 and 74 that extend in the radial direction of the primary shaft 31 and open to the outer peripheral surface of the primary shaft 31 are communicated with the oil passage 71.

  The fixed sheave 34 a of the primary pulley 34 is integrally formed on the outer periphery of the intermediate portion 31 b of the primary shaft 31.

  On the other hand, the movable sheave 34b is provided so as to be movable back and forth with respect to the fixed sheave 34a. Specifically, the movable sheave 34b is formed continuously from the thick and substantially cylindrical inner cylindrical portion 34c and the end of the inner cylindrical portion 34c on the fixed sheave 34a side, and the V A radial direction portion 34d that forms a groove, and an outer cylindrical portion 34f that extends from the position near the outer peripheral end of the radial direction portion 34d toward the Rr direction, that is, toward the outer peripheral portion 75c of the cylinder member 75. ing. An annular protrusion 34g whose outer peripheral surface abuts on the inner peripheral surface of the outer peripheral portion 75c of the cylinder member 75 is formed in the vicinity of the end portion on the Rr direction side of the outer cylindrical portion 34f. A resin seal ring 34h is attached to the outer periphery of the annular protrusion 34g. The inner cylinder portion 34c is formed with a through hole 34j that penetrates the inside and outside in the radial direction. The through hole 34j is open to an inner wall surface forming a hydraulic chamber 70 described later.

  The cylinder member 75 is an annular member that is mounted between the movable sheave 34 b and the Rr bearing 62. The cylinder member 75 is fitted into the rear end portion 31c of the primary shaft 31 and extends radially outward, and a cylindrical outer peripheral portion 75c that comes into contact with the annular protrusion 34g of the movable sheave 34b. The curved portion 75b extends from the outer peripheral end of the radial portion 75a while being curved toward the outer peripheral side, and connects the radial portion 75a and the outer peripheral portion 75c. A space surrounded by the movable sheave 34 b and the cylinder member 75 is formed as a hydraulic chamber 70 for generating a clamping pressure by the sheaves 34 a and 34 b on the V belt 33.

  A groove 34e extending in the axial direction is formed on the inner peripheral surface of the inner cylindrical portion 34c of the movable sheave 34b. On the other hand, a groove 31e extending in the axial direction is formed on the outer peripheral surface of the intermediate portion 31b of the primary shaft 31. A plurality of the grooves 34e and 31e are formed at predetermined intervals in the circumferential direction. The movable sheave 34b and the primary shaft 31 are positioned so that the groove 34e on the movable sheave 34b side and the groove 31e on the primary shaft 31 side have the same phase in the circumferential direction, and straddle both the grooves 34e and 31e. A plurality of balls (not shown) are arranged. As a result, the movable sheave 34b can move smoothly relative to the primary shaft 31, in other words, relative to the fixed sheave 34a on the primary shaft 31 in the axial direction, but relative to the circumferential direction. It is impossible to move.

  The hydraulic pressure from the hydraulic actuator 36 is supplied to the hydraulic chamber 70 via the oil passage 71. Here, the hydraulic pressure from the hydraulic actuator 36 is supplied through the oil passage 73 and the through hole 34j in the case of the upper half in FIG. 2 and the oil passage 74 in the case of the lower half in FIG. It is like that. The hydraulic pressure in the hydraulic chamber 70 acts toward the fixed sheave 34a side (in this case, the Fr direction side) with respect to the movable sheave 34b. When the hydraulic pressure in the hydraulic chamber 70 acts on the movable sheave 34 b, the movable sheave 34 b receives a pressing force toward the fixed sheave 34 a, whereby the clamping pressure by both sheaves 34 a and 34 b is applied to the V belt 33. Is granted.

  Further, when the axial position of the movable sheave 34b on the primary shaft 31 is determined according to the oil pressure in the hydraulic chamber 70 and the oil pressure in the hydraulic chamber 70 changes, the movable sheave 34b is fixed on the primary shaft 31 by a fixed sheave. Move forward and backward with respect to 34a. Accordingly, the V-groove width between the sheaves 34a and 34b is changed. Specifically, when the hydraulic pressure in the hydraulic chamber 70 increases, the movable sheave 34b moves on the primary shaft 31 to the Fr direction side. As a result, the movable sheave 34b advances (approaches) toward the fixed sheave 34a, and the V-groove width is narrowed and the winding radius of the V-belt 33 is increased as shown in the lower half of FIG. In this case, in the secondary pulley 35, the V groove width is widened, and the winding radius of the V belt 33 is small. As a result, the gear ratio in the belt type continuously variable transmission 30 is reduced. Conversely, when the oil pressure in the hydraulic chamber 70 decreases, the movable sheave 34b moves on the primary shaft 31 toward the Rr direction. As a result, the movable sheave 34b is retracted (separated) from the fixed sheave 34a, the V-groove width is increased, and the winding radius of the V-belt 33 is decreased, as shown in the upper half of FIG. In this case, in the secondary pulley 35, the V groove width is narrowed and the winding radius of the V belt 33 is increased. As a result, the gear ratio in the belt type continuously variable transmission 30 is increased.

  A radial direction portion 75a of the cylinder member 75 and an adjusting member 90 described later are interposed between the Rr bearing 62 and the step 31d of the primary shaft 31. Since the lock nut 31f is fastened to the rear end portion 31c of the primary shaft 31, the inner race 62a, the cylinder member 75, and the adjustment member 90 of the Rr bearing 62 are positioned and the rear end portion of the primary shaft 31 is positioned. It is assembled on 31c.

(Adjustment member 90)
The feature of this embodiment resides in the adjustment member 90 interposed between the step 31 d of the primary shaft 31 and the cylinder member 75. Hereinafter, the adjustment member 90 will be described in detail.

  FIG. 3 is an enlarged cross-sectional view showing the location where the adjusting member 90 is disposed and its periphery. As shown in FIG. 3, the step 31d of the primary shaft 31 includes an outer peripheral surface of the intermediate portion 31b as a large diameter portion of the primary shaft 31, an outer peripheral surface of the rear end portion 31c as a small diameter portion, and It is formed of an annular surface (contact surface) 31g that connects the outer peripheral surfaces and extends in a substantially radial direction.

  The adjusting member 90 is sandwiched between the annular surface 31g forming the step 31d and the radial portion 75a of the cylinder member 75.

  FIG. 4 is a perspective view of the adjustment member 90. As shown in FIG. 4, the adjustment member 90 is made of metal and is formed as a substantially annular member. The inner peripheral side is a shim function portion 91, and the outer peripheral side is a stopper function portion 92.

  The shim function portion 91 is an annular portion whose thickness dimension (dimension T1 in FIG. 4) is set to be relatively small, and the shim function portion 91 has an annular surface 31g forming the step 31d. And the radial portion 75a of the cylinder member 75. That is, the annular surface 31g is positioned on the Fr direction side with respect to the cylinder member 75 by the thickness dimension (T1) of the shim function portion 91, and thereby the position of the primary shaft 31 in the axial center direction is defined. Will be. Note that the inner diameter dimension of the shim function portion 91 (the inner diameter dimension of the adjustment member 90: dimension T3 in FIG. 4) substantially matches the outer diameter dimension of the rear end portion 31c of the primary shaft 31 or the rear end thereof. The outer diameter of the portion 31c is set slightly larger. The adjustment member 90 is incorporated in the primary shaft 31 so that the rear end portion 31c of the primary shaft 31 is inserted inside the shim function portion 91 (the central hole 93 of the adjustment member 90). That is, the shim function portion 91 has an Fr direction side surface 91a in contact with the annular surface 31g, an Rr direction side surface 91b in contact with the radial direction portion 75a of the cylinder member 75, and an inner peripheral surface thereof. 91c is incorporated in a state of substantially contacting the outer peripheral surface of the rear end portion 31c of the primary shaft 31.

  Further, the outer diameter dimension of the shim function portion 91 (matching the inner diameter dimension of the stopper function portion 92) substantially matches the outer diameter dimension of the intermediate portion 31b of the primary shaft 31, or the outer diameter of the intermediate portion 31b. It is set slightly larger than the diameter dimension.

  On the other hand, the stopper function portion 92 has a surface 92a on the Rr direction side that is flush with the surface 91b on the Rr direction side of the shim function portion 91, and has a thickness dimension (dimension in the axial direction: T2). The shim function portion 91 is formed of an annular portion set larger than the thickness dimension (T1). As described above, the outer diameter size of the shim function portion 91 is substantially equal to the outer diameter size of the intermediate portion 31b of the primary shaft 31 or is set slightly larger than the outer diameter size of the intermediate portion 31b. Therefore, the inner diameter dimension of the stopper function portion 92 is also substantially equal to the outer diameter dimension of the intermediate portion 31b of the primary shaft 31, or is set slightly larger than the outer diameter size of the intermediate portion 31b. become. That is, the stopper function part 92 subtracts a predetermined dimension from the outer peripheral end of the annular surface 31g forming the step 31d of the primary shaft 31 toward the movable sheave 34b (dimension T4 in FIG. 4: dimension T1 from the dimension T2 in FIG. 4). ) So as to cover the outer peripheral side of the intermediate portion 31b of the primary shaft 31. In other words, since the region on the outer peripheral side of the intermediate portion 31b of the primary shaft 31 is a moving space for the inner cylindrical portion 34c of the movable sheave 34b, one end portion of this moving space (one end portion on the Rr direction side). Since the stopper function part 92 is present on the primary shaft 31, the movable range (movable range in the Rr direction) of the movable sheave 34b on the primary shaft 31 is regulated. In other words, the movable range of the movable sheave 34b is set to the position where the end surface (the left end surface in FIG. 3) of the movable sheave 34b contacts the stopper function portion 92. In other words, the Fr direction side surface 92b of the stopper functioning part 92 functions as a stopper surface for the retreating side end surface of the movable sheave 34b, the Rr direction side surface 92a abuts the cylinder member 75, The inner peripheral surface 92c is incorporated in a state of being substantially in contact with the outer peripheral surface of the intermediate portion 31b of the primary shaft 31.

  In this embodiment, the adjustment member 90 including the shim function portion 91 and the stopper function portion 92 as described above is provided in a plurality of types (thickness dimensions T1 of the shim function portion 91 are different from each other and the stopper function portion 92 (Those having different thickness dimensions T2) are prepared, and when the belt-type continuously variable transmission 30 is assembled, one of the plurality of types of adjusting members 90 is selected and assembled to the primary shaft 31. It has become. This will be specifically described below.

  For example, when producing five models having different displacements as the engine 1 connected to the belt-type continuously variable transmission 30, five types having different thicknesses of the stopper function portion 92 according to each model. The same stopper function part group (a set of adjustment members 90 having the same thickness dimension of the stopper function part 92) is set, and in each stopper function part group, the thickness dimension of the stopper function part 92 is the same. Also, eight types of adjustment members having different thickness dimensions of the shim function portion 91 are prepared.

  That is, there are eight types of adjusting members 90 having a difference in thickness dimension of the shim function portion 91 for each of five types of stopper function portion groups having a difference in thickness dimension of the stopper function portion 92, that is, a total of 40 types of adjustment members 90. It is prepared.

  To illustrate specific numerical values, for example, there is a shim for a first stopper function unit group (a set of adjustment members 90 having a thickness dimension of 2 mm of the stopper function part 92) in which the thickness dimension of the stopper function part 92 is 2 mm. The thickness of the functional part 91 is 1.00 mm, 1.05 mm, 1.10 mm, 1.15 mm, 1.20 mm, 1.25 mm, 1.30 mm, Eight types are prepared such as 1.35 mm.

  In addition, the second stopper function part group in which the thickness dimension of the stopper function part 92 is 4 mm includes the shim function part 91 having a thickness dimension of 1.00 mm, 1.05 mm, and 1.10 mm. Eight types are prepared such as 1.15 mm, 1.20 mm, 1.25 mm, 1.30 mm, and 1.35 mm.

  Hereinafter, similarly, in the third stopper function part group in which the thickness dimension of the stopper function part 92 is 6 mm, eight types having different thickness dimensions of the shim function part 91 are prepared. In the fourth stopper function part group having a dimension of 8 mm, eight types having different thickness dimensions of the shim function part 91 are prepared, and in the fifth stopper function part group having a thickness dimension of the stopper function part 92 of 10 mm. In addition, eight types of shim function portions 91 having different thickness dimensions are prepared.

  Each of the above dimensions is an example, and the present invention is not limited to this.

  Hereinafter, an application mode of the adjustment member 90 prepared in advance to the belt-type continuously variable transmission 30 will be described.

-First application form-
First, as one form of application of the adjustment member 90 to the belt-type continuously variable transmission 30, the optimum adjustment member 90 is selected and applied to each belt-type continuously variable transmission 30 of a different model. Is mentioned.

  For example, when five types of belt-type continuously variable transmissions 30 are produced according to each of the five types of engines 1 to be produced, according to each belt-type continuously variable transmission 30, the 40 types of adjustment members 90 are adjusted. Among them, the one having the optimum thickness dimension T1 of the shim function portion 91 and the thickness dimension T2 of the stopper function portion 92 is selected, and the selected adjustment member 90 is assembled to the primary shaft 31.

  For example, for the smallest belt-type continuously variable transmission 30 (for example, the belt-type continuously variable transmission 30 connected to the engine 1 having the smallest displacement among the five types of engines 1), the first stopper function unit. One adjusting member 90 in the group is the second smallest belt type continuously variable transmission 30, and one adjusting member 90 in the second stopper function group is the third smallest belt. For the continuously variable transmission 30, one adjusting member 90 from the third stopper function section group is provided. For the fourth smallest belt-type continuously variable transmission 30, the fourth stopper function section group is provided. One adjusting member 90 is the largest belt-type continuously variable transmission 30 (for example, the belt-type continuously variable transmission 30 connected to the engine 1 having the largest displacement among the five types of engines 1). From the fifth stopper function group One of the adjusting member 90 is to be selected.

  Further, the adjustment member 90 selected from each of the stopper function unit groups (out of the eight types of adjustment members 90) has an appropriate thickness according to an error in the component dimensions of the belt type continuously variable transmission 30 to be applied. A device having a shim function unit 91 having dimensions is selected.

-Second application form-
In addition to the first application mode described above, a second application mode described below can be cited. In the second application mode, different shift characteristics are obtained by changing the adjustment member 90 to be applied to one type of belt-type continuously variable transmission 30. This is because one type of belt-type continuously variable transmission 30 is applied to different engines 1 (for example, engines having different displacements), and an adjustment member 90 applied to this belt-type continuously variable transmission 30 is appropriately selected. Thus, the belt-type continuously variable transmission 30 is provided with a speed change characteristic corresponding to the engine 1. This will be specifically described below.

  The selection of the stopper function unit group in the second application form is performed according to the type of engine (for example, the displacement) connected to the belt type continuously variable transmission 30. For example, when producing five types of engines having different displacements, one adjustment from the first stopper function unit group is applied to the belt-type continuously variable transmission 30 applied to the engine having the smallest displacement. For the belt-type continuously variable transmission 30 that is applied to the engine having the second smallest displacement, the member 90 has the third adjustment member 90 in the second stopper function unit group, which has the third smallest displacement. For the belt-type continuously variable transmission 30 applied to the engine, one adjusting member 90 from the third stopper function unit group is applied to the engine with the fourth smallest displacement. For the belt type continuously variable transmission 30 applied to the engine having the largest displacement, the adjustment member 90 in the fourth stopper function unit group is included in the fifth stopper function unit group. From one adjustment member 0 so that is selected.

  Further, the adjustment member 90 selected from each of the stopper function unit groups (out of the eight types of adjustment members 90) has an appropriate thickness according to an error in the component dimensions of the belt type continuously variable transmission 30 to be applied. A device having a shim function unit 91 having dimensions is selected.

(Effect of embodiment)
-Effects common to each application form-
As described above, in the present embodiment, the position of the primary shaft 31 in the axial direction is the shim function portion 91 of the adjustment member 90 in both the first application mode and the second application mode described above. It is prescribed by. That is, by appropriately obtaining the position of the primary shaft 31 in the axial direction, the relative positions of the fixed sheaves 34a and 35a of the primary pulley 34 and the secondary pulley 35 can be appropriately obtained. The stretched V-belt 33 extends in a direction orthogonal to the axial extension direction of each shaft 31 and 32, and the durability of the V-belt 33 can be ensured.

  Further, when the movable sheave 34 b of the primary pulley 34 moves to the retracted position farthest from the fixed sheave 34 a, the movable sheave 34 b comes into contact with the stopper function portion 92 of the adjustment member 90. That is, the movable sheave 34b is restricted from moving backward from the contact position.

  As described above, the adjustment member 90 of the present embodiment has a shim function for adjusting the position of the primary shaft 31 in the axial direction, a function as a stopper that contacts the movable sheave 34b, and the maximum of the belt-type continuously variable transmission 30. The conventional shim (single part having only the shim function: see shim n in FIG. 5) can be abolished. Thus, in the present embodiment, the shim function, the stopper function, and the gear ratio defining function can be shared by the adjustment member 90. Conventionally, it has been necessary to individually manufacture and individually manage a shim that exhibits a shim function and a cylinder seat that exhibits a stopper function, but according to the present embodiment, this need is eliminated, and component management becomes complicated. This can be eliminated, and the production cost can be reduced.

-Effects peculiar to the second application form-
In particular, since the adjustment member 90 has a gear ratio defining function, the adjustment member to be applied even in the belt-type continuously variable transmission 30 having the same configuration as described in the second application mode. By changing 90, it is possible to construct a transmission 30 with a different maximum speed ratio.

  For example, as described above, the adjustment member 90 with a small thickness of the stopper function portion 92 is applied to the belt-type continuously variable transmission 30 connected to the small displacement engine. As a result, the maximum transmission ratio is increased so that a large transmission torque to the wheels 3 can be obtained. As a result, even when a small displacement engine is installed, it is possible to sufficiently exhibit the start acceleration performance of the vehicle.

  Conversely, the adjustment member 90 having a large thickness of the stopper function portion 92 is applied to the belt-type continuously variable transmission 30 connected to the large displacement engine. As a result, the maximum gear ratio is reduced and the engine speed is kept low. As a result, it is possible to improve the fuel consumption rate by restricting the maximum gear ratio while ensuring high running performance with a relatively large torque output from the large displacement engine.

  As described above, even in the belt-type continuously variable transmission 30 having the same configuration, the engine displacement is appropriately selected by appropriately selecting the adjustment member 90 to be applied (the adjustment member 90 having a different thickness dimension of the stopper function portion 92). Thus, the belt type continuously variable transmission 30 can be configured to have a speed change characteristic according to the above. That is, while the belt-type continuously variable transmission 30 having the same configuration is connected to various engines (engines having different displacements), the speed change characteristics of the belt-type continuously variable transmission 30 can be selected by appropriately selecting the adjustment member 90. Can be adjusted to characteristics according to the engine. Accordingly, the versatility of one type of belt-type continuously variable transmission 30 can be greatly expanded (shift characteristics according to various engines can be obtained), and the belt-type continuously variable transmission 30 for each type of engine 1. Need not be individually designed, and it is not necessary to individually manufacture the components of the belt-type continuously variable transmission 30 for each type of the engine 1, so that significant cost reduction can be achieved.

-Other embodiments-
In the embodiment described above, the case where the present invention is applied to the belt type continuously variable transmission 30 for automobiles has been described. The present invention is not limited to this, and can also be applied to a belt-type continuously variable transmission used for purposes other than automobiles. Further, the present invention is applicable not only to automobiles using a gasoline engine as a drive source but also to belt-type continuously variable transmissions mounted on automobiles and hybrid cars using a diesel engine as a drive source.

  Further, in the above embodiment, the thickness dimension of the shim function portion 91 and the stopper function portion 92 in the adjustment member 90 is larger in the stopper function portion 92 than in the shim function portion 91. The present invention is not limited to this, and depending on the setting of the maximum transmission ratio of the belt-type continuously variable transmission 30, the thickness dimension of the shim function portion 91 and the thickness dimension of the stopper function portion 92 are substantially the same dimension, In some cases, the thickness dimension of the stopper function portion 92 is smaller than that of the shim function portion 91.

  In the above embodiment, the case where the adjustment member 90 is mounted on the primary shaft 31 has been described. However, the adjustment member may be mounted on the secondary shaft 32.

It is a skeleton figure which shows the whole structure of the transaxle to which the belt type continuously variable transmission which concerns on embodiment is applied. It is sectional drawing which shows the structure of the primary shaft and its peripheral part of a belt-type continuously variable transmission. It is sectional drawing which expands and shows the arrangement | positioning location of an adjustment member, and its periphery. It is a perspective view of an adjustment member. It is sectional drawing which shows the structure of the primary shaft in the conventional belt-type continuously variable transmission, and its peripheral part.

Explanation of symbols

1 engine (internal combustion engine)
30 Belt type continuously variable transmission 31 Primary shaft (shaft member)
31b Middle part (large diameter part)
31c Rear end (small diameter part)
31f Lock nut 31g Annular surface (contact surface)
32 Secondary shaft (shaft member)
33 V belt (belt means)
34 Primary pulley (drive pulley)
35 Secondary pulley (driven pulley)
34a, 35a Fixed sheave 34b, 35b Movable sheave 62 Rr bearing (bearing)
62a Inner race 90 Adjustment member 91 Shim function part 92 Stopper function part

Claims (4)

One of a pair of shaft members parallel to each other is provided with a driving pulley having a fixed sheave and a movable sheave, and the other is provided with a driven pulley having a fixed sheave and a movable sheave. The belt means is stretched so that the rotational force of the driving pulley can be transmitted to the driven pulley via the belt means, and each movable sheave moves forward and backward toward the fixed sheave. In the belt type continuously variable transmission in which the gear ratio can be changed by changing the winding position of the belt means in the radial direction of each pulley,
An adjustment member is attached to at least one of the shaft members, and the adjustment member defines a position in the axial direction of the shaft member by contacting an abutting surface extending in a substantially radial direction on the shaft member. A shim function part, and a stopper function part that defines the last retracted position of the movable sheave by contacting the movable sheave when the movable sheave moves away from the fixed sheave ;
The adjustment member is mounted on the shaft member by selecting one from a plurality of types having different thickness dimensions in the axial direction of the shim function portion and different thickness dimensions in the axial direction of the stopper function portion. belt type continuously variable transmission, characterized in that there. In the belt type continuously variable transmission according to claim 1,
The adjusting member is attached to a shaft member provided with a driving pulley.
The adjusting member attached to the shaft member is selected from a plurality of types of adjusting members having different thicknesses of the stopper function portion according to the model of the internal combustion engine to be connected. A belt type continuously variable transmission. In the belt type continuously variable transmission according to claim 1 or 2,
The shaft member includes a large-diameter portion where the movable sheave moves forward and backward, a small-diameter portion formed closer to the movable sheave than the large-diameter portion, and a large radius connecting the large-diameter portion and the small-diameter portion. The contact surface extending in the direction is formed,
The shim function portion of the adjustment member is made of an annular plate material having an inner diameter dimension that substantially matches the outer diameter dimension of the small diameter portion, and the stopper function portion is formed continuously on the outer peripheral side of the shim function portion and It consists of an annular member having an inner diameter that substantially matches the outer diameter of the large diameter portion,
The position of the shaft member in the axial direction is defined by abutting the shim function portion of the adjustment member on the abutment surface. On the outer peripheral side of the shim function portion, the stopper function portion is the outer periphery of the large diameter portion. A belt type continuously variable transmission characterized in that the last retracted position of the movable sheave is defined by being located on the side. In the belt type continuously variable transmission according to claim 1, 2, or 3,
A bearing for rotatably supporting the shaft member is disposed at one end portion of the shaft member, and a locking nut is attached to a male screw portion formed at the one end portion of the shaft member, so that the fastening force is increased. However, the belt-type continuously variable transmission is characterized in that the shim function portion is pressed against the contact surface of the shaft member through an inner race of the bearing.

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