JP2019173903A - Belt-type continuous variable transmission - Google Patents

Abstract

To provide a belt-type continuously variable transmission which can be reduced size and weight without narrowing a change width of a gear change ratio which can be set by the belt-type continuously variable transmission.SOLUTION: In a belt-type continuously variable transmission 1, one-side side faces 23P1, 23S1 of spline grooves 23P3, 23S3 are formed so as to be torsional with respect to an axial line direction so that groove widths of the spline grooves 23P3, 23S3 are narrowed toward fixed sheave 7, 13 sides from movable sheave 8, 14 sides, the other side faces 22P1, 22S1 of spline teeth 22P, 22S oppose to the one-side side faces 23P1, 23S1 and formed in parallel with each other, and when the movable sheaves 8, 14 move to the fixed sheave 7, 13 sides, the respective side faces 23P1, 23S1 and 22P1, 22S1 abut on each other, thus inhibiting movement of the movable sheaves 8, 14.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a belt-type continuously variable transmission that includes a pair of pulleys and a belt wound around the pulleys, and that continuously changes a gear ratio by changing a belt wrapping radius. is there.

  An example of this type of belt-type continuously variable transmission is described in Patent Document 1. Each pulley of the belt type continuously variable transmission includes a fixed sheave integrally formed with the rotating shaft and a movable sheave that rotates integrally with the rotating shaft and moves back and forth in the axial direction with respect to the fixed sheave. The belt is wound around the V groove of each pulley formed by each sheave. The stationary sheave of the driving pulley and the movable sheave of the driven pulley are arranged adjacent to each other in the inter-axis distance direction between the pulleys, and similarly, the movable sheave and the driven pulley of the driving pulley in the inter-axis distance direction. The stationary sheaves of the side pulleys are arranged adjacent to each other. The outer diameter of the movable sheave is formed smaller than the outer diameter of the fixed sheave, and at least a part of the fixed sheave of the driving pulley and at least a part of the fixed sheave of the driven pulley are in the axial direction. Are arranged to overlap each other. Further, in the configuration described in Patent Document 1, a step portion is formed on the rotation shaft, and a cylindrical boss portion formed on the inner peripheral side of the movable sheave contacts the step portion, thereby fixing the step. Movement of the movable sheave to the sheave side is restricted. That is, the fixed sheave side of the rotating shaft is formed with a large diameter corresponding to the stepped portion.

JP 2011-185405 A

  In the belt-type continuously variable transmission having the above-described configuration, when the movable sheave approaches the fixed sheave and the groove width of the V-groove between them decreases, the belt winding radius increases, and the fixed sheave On the other hand, if the movable sheave approaches too much, the wrapping radius of the belt becomes larger than the outer diameter of each sheave, and the belt may fall off from each pulley. For this reason, in the configuration described in Patent Document 1, the position of the movable sheave with respect to the fixed sheave in the axial direction is regulated by bringing the boss portion of the movable sheave into contact with the stepped portion provided on the rotating shaft. The maximum hook radius is set. By the way, the outer diameter, that is, the rigidity and the strength of the rotating shaft is determined by design according to the magnitude of the torque transmitted by the rotating shaft. For this reason, when a step portion is provided on the rotation shaft, the rotation shaft becomes thicker by the step portion, and accordingly, the inner diameter and outer diameter of each sheave increase. As described above, in the configuration described in Patent Document 1, there is still room for improvement in order to reduce the size and weight of the belt-type continuously variable transmission.

  The present invention has been made paying attention to the above technical problem, and can be reduced in size and weight without reducing the change width of the transmission ratio that can be set by the belt-type continuously variable transmission. The object is to provide a step transmission.

  In order to achieve the above object, the present invention provides a fixed sheave integrated with a rotating shaft, and a spline that fits in a spline groove formed on an outer peripheral surface of the rotating shaft along the axial direction of the rotating shaft. A pair of teeth each having a movable sheave that rotates integrally with the rotary shaft and moves toward and away from the fixed sheave in the axial direction when the spline teeth are fitted in the spline groove. And a belt-type continuously variable transmission that is wound around the pair of pulleys and transmits a torque between the pair of pulleys. One side surface of both side surfaces of the spline groove is formed to be twisted with respect to the axial direction so as to narrow toward the fixed sheave side, and the spline teeth The other side surface of the both side surfaces of the spline teeth is opposed to the one side surface so that the thickness decreases from the side opposite to the fixed sheave toward the fixed sheave side. Formed parallel to each other, and configured to prevent movement of the movable sheave by contacting the one side surface and the other side surface when the movable sheave moves toward the fixed sheave side in the axial direction. It is characterized by being.

  According to this invention, one side surface of the spline groove formed on the outer peripheral surface of the rotating shaft is twisted with respect to the axial direction so that the groove width on the fixed sheave side is narrower than the groove width on the movable sheave side. The other side surface of the spline teeth formed on the inner peripheral surface of the movable sheave is opposed to one side surface of the spline groove and is formed in parallel with one side surface of the spline groove. That is, the spline teeth are formed such that the tooth thickness gradually decreases from the side opposite to the fixed sheave toward the fixed sheave side. Therefore, when the movable sheave moves toward the fixed sheave in the axial direction of the rotating shaft, one side surface of the spline groove and the other side surface of the spline teeth finally come into contact with each other to prevent the movement of the movable sheave. The That is, one side surface of the spline groove and the other side surface of the spline teeth function as a stopper that prevents the movement of the movable sheave. Therefore, it is not necessary to provide a structure for preventing the movement of the movable sheave on the outer peripheral side of the rotating shaft, and each rotating shaft can be made as thin as possible because there is no such protruding portion. Accordingly, the inner diameter and outer diameter of each sheave can be reduced, or only the inner diameter of each sheave can be reduced. For example, when both the inner and outer diameters of each sheave are reduced, the change width of the belt wrapping radius is maintained, so the change ratio change width that can be set as a belt-type continuously variable transmission is changed. Or it does not shrink. The pulleys can be arranged close to each other while maintaining a changeable range of the change gear ratio, thereby reducing the distance between the shafts of the pulleys. In addition, each sheave can be reduced in weight as the diameter of each sheave is reduced. On the other hand, when only the inner diameter of each sheave is reduced, the minimum radius position around which the belt of each pulley is wound can be expanded inward in the radial direction to increase the changeable range of the changeable gear ratio. . As a result, the belt-type continuously variable transmission can be reduced in size and weight without reducing the changeable range of the changeable gear ratio.

It is a figure which shows typically an example of a structure of the belt-type continuously variable transmission which concerns on this invention. It is sectional drawing which shows a part of each sheave. It is a figure which shows an example of a structure of a 1st spline tooth, and an example of a structure of a 2nd spline tooth. It is sectional drawing which shows the fitting state of a 1st spline tooth | gear and a spline groove | channel. FIG. 5A is a diagram for explaining a fitting state between the first spline teeth and the spline grooves, and FIG. 5A shows that the movable sheave can move back and forth in the axial direction, and the first spline teeth and the spline grooves are fitted. FIG. 5B is a diagram for explaining a state in which the first spline teeth and the spline grooves are in contact with or engaged with each other so as to prevent the movement of each movable sheave. is there.

  A belt-type continuously variable transmission according to an embodiment of the present invention includes a pair of pulleys that transmit torque by frictional force generated by pinching a belt, and continuously changes the wrapping radius of the belt with respect to each pulley. Thus, the transmission gear ratio is changed continuously, that is, steplessly. FIG. 1 shows an example of the configuration of a belt type continuously variable transmission according to an embodiment of the present invention. A belt type continuously variable transmission (hereinafter referred to as CVT) 1 shown in FIG. 1 is configured in the same manner as a conventionally known one, and an input shaft to which torque is transmitted from a power source such as an engine (not shown). 2, a primary pulley 3 connected to 2, a secondary pulley 5 connected to an output shaft 4 that transmits torque to an output member such as a drive wheel (not shown), and an endless belt wound around these pulleys 3, 5. 6. Note that the input shaft 2 and the output shaft 4 described above are arranged in parallel.

  The primary pulley 3 includes a conical first fixed sheave 7 and a first movable sheave 8, and the first fixed sheave 7 is formed integrally with the input shaft 2. The first movable sheave 8 is spline-fitted to the input shaft 2. That is, the first fixed sheave 7 is integrated with the input shaft 2, and the first movable sheave 8 rotates integrally with the input shaft 2 and approaches or separates from the first fixed sheave 7. The conical surfaces 9 and 10 of the sheaves 7 and 8 face each other in the axial direction of the input shaft 2, and the first V groove 11 is formed by the conical surfaces 9 and 10.

  A first hydraulic actuator 12 is provided on the back side of the first movable sheave 8, that is, on the side opposite to the conical surface 10 in the axial direction. In the example shown here, the first hydraulic actuator 12 is configured to press the first movable sheave 8 toward the first fixed sheave 7 in the axial direction when oil is supplied.

  The secondary pulley 5 is also configured in the same manner as the primary pulley 3, that is, includes a conical second fixed sheave 13 and a second movable sheave 14, and the second fixed sheave 13 is integrated with the output shaft 4. Is formed. The second movable sheave 14 is spline-fitted to the output shaft 4. That is, the second fixed sheave 13 is integrated with the output shaft 4, and the second movable sheave 14 rotates integrally with the output shaft 4 and approaches or separates from the second fixed sheave 13. The conical surfaces 15 and 16 of the sheaves 13 and 14 are arranged to face the output shaft 4 in the axial direction, and the second V groove 17 is formed by the conical surfaces 15 and 16.

  A second hydraulic actuator 18 is provided on the back side of the second movable sheave 14, that is, on the side opposite to the conical surface 16 in the axial direction. In the example shown here, the second hydraulic actuator 18 is configured to press the second movable sheave 14 toward the second fixed sheave 13 in the axial direction when oil is supplied.

  In addition, a distance between the rotation center axes of the pulleys 3 and 5 (hereinafter referred to as an inter-axis distance) between the first fixed sheave 7 of the primary pulley 3 and the second movable sheave 14 of the secondary pulley 5 in the L direction. The primary pulley 3 and the secondary pulley 5 are arranged so that the first movable sheave 8 of the primary pulley 3 and the second fixed sheave 13 of the secondary pulley 5 are adjacent to each other.

  Further, the belt 6 is wound around the primary pulley 3 and the secondary pulley 5 configured as described above, that is, across the V-grooves 11 and 17. In the example shown here, the belt 6 is referred to as a push belt, and is configured in substantially the same manner as conventionally known. That is, the plurality of elements 19 are arranged in an annular shape with the directions thereof aligned, and are bound by the ring 20.

  Here, the configuration of the fixed sheaves 7 and 13 and the configuration of the movable sheaves 8 and 14 will be specifically described. In FIG. 2, a part of each sheave 7, 8, 13, 14 is shown in cross section. The first fixed sheave 7 and the second fixed sheave 13 are formed in substantially the same shape, and the first movable sheave 8 and the second movable sheave 14 are formed in substantially the same shape. Therefore, in the following description, the configuration on one side, for example, the primary pulley 3 side will be described, and the description of the configuration on the other side, that is, the secondary pulley 5 side, similar to the primary pulley 3 will be omitted. For the same configuration in each of the pulleys 3 and 5, in FIG. 2, “P” is added to the reference symbol of the configuration on the primary pulley 3 side, and “S” is added to the reference symbol of the configuration on the secondary pulley 5 side. It is.

  First, the configuration of each movable sheave 8, 14 will be described. As shown in FIG. 2, the inner periphery of each movable sheave 8, 14 is on the back side of each movable sheave 8, 14, that is, on the left side in FIG. The extended cylindrical boss portions 21P and 21S are integrally formed. First spline teeth 22P and 22S are formed on the inner peripheral surfaces of the boss portions 21P and 21S at regular intervals in the circumferential direction. The first spline teeth 22P and 22S extend in the axial direction, and as will be described later, their tooth thickness gradually increases from the end on the fixed sheave 8 and 14 side toward the opposite end. Has been. Each first spline tooth 22P, 22S is subjected to so-called involute processing, and the tooth thickness gradually decreases from the tooth base toward the tooth tip. The first spline teeth 22P and 22S described above correspond to the spline teeth in the embodiment of the present invention.

  The first fixed sheave 7 and the second fixed sheave 13 are integrally formed at one end of the input shaft 2 and the output shaft 4, respectively, and the outer peripheral surface of the substantially central portion in the axial direction of each shaft 2, 4. In addition, second spline teeth 23P and 23S are formed. As will be described later, the first spline teeth 22P and 22S described above are fitted into the spline grooves between the second spline teeth 23P and 23S adjacent to each other. Further, the tooth thickness of the second spline teeth 23P, 23S is formed so as to become gradually thinner from the fixed sheaves 8, 14 side toward the movable sheaves 7, 13 side. Further, like the first spline teeth 22P and 22S, so-called involute processing is performed on the second spline teeth 23P and 23S, and the tooth thickness gradually decreases from the tooth base toward the tooth tip.

  In the example shown here, the angle formed between the rotation center axis of each of the shafts 2 and 4 and the conical surfaces 9 and 15 of the respective fixed sheaves 7 and 13 is set to be larger than in the prior art. Further, the angle formed between the rotation center axis of each of the shafts 2 and 4 and the conical surfaces 10 and 16 of the respective movable sheaves 8 and 14 is set to be larger than that in the prior art. This is to maintain the interval between the movable sheaves 8 and 14 when they are closest to the fixed sheaves 7 and 13 at a predetermined interval, as will be described later.

  The configuration for supplying oil to the hydraulic actuators 12 and 18 will be briefly described. The input shaft 2 and the output shaft 4 are predetermined from the other end of the shafts 2 and 4 as shown in FIG. The hollow portions 24P and 24S having a long length are formed. The first through holes 25P and 25S penetrating the input shaft 2 in the plate thickness direction are formed at the tip portions of the hollow portions 24P and 24S, that is, the right portion in FIG. Second through holes 26P and 26S are formed on the opposite side of the fixed sheaves 7 and 13 with the first through holes 25P and 25S interposed therebetween. Further, third through holes 27P and 27S communicating with hydraulic chambers (not shown) of the hydraulic actuators 12 and 18 are formed in the boss portions 21P and 21S of the movable sheaves 8 and 14, respectively. A hydraulic source such as an oil pump (not shown) is connected to the openings of the hollow portions 24P and 24S. Therefore, when the first through holes 25P, 25S and the second through holes 26P, 26S communicate with the third through holes 27P, 27S, the respective through holes 25P, 25S, 26P, 26S, 27P, 27S are connected to each other. Oil is supplied to the hydraulic actuators 12 and 18 from a hydraulic source, and the oil is discharged to a drain location (not shown). As a result, the movable sheaves 8 and 14 move back and forth in the axial direction.

  Next, the shapes of the spline teeth 22P and 22S and the shapes of the second spline teeth 23P and 23S will be described more specifically. An example is shown in FIG. FIG. 4 is a cross-sectional view showing a state in which the first spline teeth 22P and 22S and the second spline teeth 23P and 23S are fitted. First, the shape of each of the second spline teeth 23P, 23S will be described. Since the second spline teeth 23P, 23S are subjected to involute processing as described above, as shown in FIG. 3 and FIG. The tooth thickness of the second spline teeth 23P and 23S is tapered from the tooth base toward the tooth tip. Further, the tooth thickness on the fixed sheaves 7 and 13 side of the second spline teeth 23P and 23S in the axial direction is formed thicker than the tooth thickness on the movable sheaves 8 and 14 side as shown in FIG. . That is, the second spline teeth 23P and 23S are formed so as to gradually become thinner from the fixed sheaves 7 and 13 side toward the movable sheaves 8 and 14, respectively.

  Specifically, as shown in FIG. 3, one side surface of both side surfaces 23P1, 23P2, 23S1, 23S2 of the second spline teeth 23P, 23S in the circumferential direction, referred to as a contact surface or a tooth surface. 23P1 and 23S1 are formed to be twisted or inclined at a predetermined angle with respect to the axial direction. The other side surfaces 23P2 and 23S2 are formed substantially parallel to the axial direction. The magnitude of the twist angle of one of the side surfaces 23P1 and 23S1 can be determined in advance in design.

  Between the second spline teeth 23P and 23S adjacent to each other in the circumferential direction, spline grooves 23P3 and 23S3 into which the first spline teeth 22P and 22S are fitted are formed. Therefore, the groove widths of the spline grooves 23P3 and 23S3 are gradually narrowed from the movable sheaves 8 and 14 side toward the fixed sheaves 7 and 13 side in the axial direction. The spline grooves 23P3 and 23S3 described above correspond to the spline grooves in the embodiment of the present invention, and the one side surfaces 23P1 and 23S1 of the second spline teeth 23P and 23S described above are the spline grooves in the embodiment of the present invention. It corresponds to one side.

  The first spline teeth 22P and 22S are engaged with the second spline teeth 23P and 23S or the spline grooves 23P3 and 23S3 when the movable sheaves 8 and 14 move toward the fixed sheaves 7 and 13 in the axial direction. The sheaves 8 and 14 are configured to stop moving. In the example shown here, each of the first spline teeth 22P and 22S is formed longer in the axial direction than each of the second spline teeth 23P and 23S, and is configured to fit into the spline grooves 23P3 and 23S3. ing. That is, the tooth thickness on the one end side of each fixed sheave 7, 13 of each first spline tooth 22P, 22S is substantially the same as the groove width on each fixed sheave 7, 13 side of spline groove 23P3, 23S3 or the groove width. The tooth thickness on the other end side of each first spline tooth 22P, 22S is set to be substantially the same as or thicker than the groove width on each movable sheave 8, 14 side of the spline grooves 23P3, 23S3. ing. That is, the first spline teeth 22P and 22S are formed so that the tooth thickness gradually increases from the right side to the left side in FIG. 3 in contrast to the second spline teeth 23P and 23S.

  Specifically, as shown in FIG. 3, one side surface of both side surfaces 22P1, 22P2, 22S1, and 22S2 of the first spline teeth 22P and 22S in the circumferential direction, referred to as a contact surface or a tooth surface. 22P1 and 22S1 are formed so as to face the one side surface 23P1 and 23S1 and be parallel to each other, that is, twisted at a predetermined angle with respect to the axial direction. The other side surfaces 22P2 and 22S2 of the first spline teeth 22P and 22S are formed substantially parallel to the axial direction, and face the other side surfaces 23P2 and 23S2. As described above, the tooth thickness on the other end side of each first spline tooth 22P, 22S is substantially the same as or larger than the groove width of the spline grooves 23P3, 23S3. When the movable sheaves 8 and 14 move, the side surfaces 23P1 and 23S1 and the side surfaces 22P1 and 22S1 of the first spline teeth 22P and 22S finally come into contact with or engage with each other.

  Next, the operation of the CVT 1 configured as described above will be described. The CVT 1 configured as described above is configured to change the transmission gear ratio by changing the winding radius of the belt 6 wound around the primary pulley 3 and the secondary pulley 5. Therefore, for example, when the amount of oil supplied to the first hydraulic actuator 12 is increased in accordance with the required gear ratio, the pressing force generated by the first hydraulic actuator 12 increases and moves toward the first fixed sheave 7 in the axial direction. The first movable sheave 8 moves. That is, as shown in FIG. 5A, the first spline teeth 22P move in the spline grooves 23P3 between the adjacent second spline teeth 23P toward the first fixed sheave 7 side. By doing so, the groove width of the first V-groove 11 is gradually narrowed, and the wrapping radius of the belt 6 at the primary pulley 2 is gradually increased. Further, with the movement of the first spline teeth 22P toward the first fixed sheave 7 side, the gap between the first spline teeth 22P and the second spline teeth 23P is gradually narrowed.

  As described above, the tooth thickness on the other end side of each first spline tooth 22P, 22S is set to be substantially the same as or wider than the groove width on the movable sheave 8, 14 side in the spline groove 23P3. Therefore, when the movable sheaves 8 and 14 further move toward the fixed sheaves 7 and 13, finally, as shown in FIG. 4 and FIG. 5B, one side 22P1 of the first spline teeth 22P One side surface 23P1 of the second spline teeth 23P comes into contact with and engages. That is, the first spline teeth 22P are sandwiched between the second spline teeth 23P adjacent to each other, or the first spline teeth 22P are fitted into the spline grooves 23P3 to prevent the movement of the first movable sheave 8 or Stopped. Since the circumference of the belt 6 is constant, as described above, when the wrapping radius of the belt 6 is increased in the primary pulley 3, the second V groove 17 is pushed and widened by the belt 6 in the secondary pulley 5. The winding radius of becomes gradually smaller. That is, when the groove width of the first V groove 11 is changed, the groove width of the second V groove 17 is changed accordingly.

  On the other hand, when the amount of oil supplied to the first hydraulic actuator 12 is decreased, the pressing force generated by the first hydraulic actuator 12 is decreased and the first movable sheave 8 is separated from the first fixed sheave 7. And the groove width of the 1st V groove 11 becomes large gradually, and the winding radius of the belt 6 in the primary pulley 3 becomes small gradually. On the other hand, in the secondary pulley 5, the second movable sheave 14 approaches the second fixed sheave 13, the groove width of the second V groove 17 gradually decreases, and the winding radius of the belt 6 gradually increases. That is, the first spline teeth 22S move in the spline grooves 23S3 between the adjacent second spline teeth 23S toward the second fixed sheave 7 side. Finally, one side surface 22S1 of the first spline tooth 22S and one side surface 23S1 of the second spline tooth 23S come into contact with or engage with each other. That is, the first spline teeth 22S are sandwiched between the second spline teeth 23S adjacent to each other, or the first spline teeth 22S are fitted in the spline grooves 23S3 to prevent the movement of the second movable sheave 14 or Stopped.

  As described above, according to the CVT 1 according to the present invention, the first spline teeth 22P1 and 22S and the second spline teeth 23P and 23S abut or engage with each other, thereby preventing the movement of the movable sheaves 8 and 14. Or stop. That is, since each spline tooth 22P1, 22S, 23P, 23S has a function as a stopper, there is no need to provide a structure for stopping each movable sheave 8, 14 so as to protrude outside each shaft 2, 4. Since there is no such protruding portion, the diameters of the shafts 2 and 4 can be made smaller than before, and the shapes of the shafts 2 and 4 can be simplified. Further, the inner diameters of the pulleys 3 and 5 can be reduced by reducing the diameters of the shafts 2 and 4. That is, the minimum radial position where the belt 6 is wound around each pulley 3 and 5 can be expanded inward in the radial direction. Therefore, when the outer diameters of the pulleys 3 and 5 are maintained, the changeable range of the changeable gear ratio can be expanded without increasing the size of the CVT 1. Further, as the inner diameters of the pulleys 3 and 5 are reduced, their outer diameters can be reduced. In this case, the pulleys 3 and 5 can be arranged close to each other, whereby the inter-axis distance L can be shortened. As a result, it is possible to reduce the size of CVT 1 without reducing or changing the change width of the transmission ratio that can be set by CVT 1. Further, the CVT 1 can be reduced in weight as the diameters of the pulleys 3 and 5 are reduced.

  Moreover, in CVT1 of the structure mentioned above, the angle which the rotation center axis line of each pulley 3 and 5 and each conical surface 9,10,15,16 comprise is set largely compared with the past. Therefore, even if the movable sheaves 8 and 14 are brought closest to the fixed sheaves 7 and 13, the inner ends of the movable sheaves 8 and 14 in the radial direction and the distal end portions on the fixed sheaves 7 and 13 side in the axial direction By keeping the shortest distance between the distal end of the movable sheaves 8 and 14 in the axial direction and the inside of the fixed sheaves 7 and 13 in the radial direction, the contact between them can be suppressed. it can.

  The embodiment of the present invention has been described above. However, the present invention is not limited to the above-described example, and may be appropriately changed within the scope of achieving the object of the present invention. That is, the spline grooves 23P3 and 23S3 and the spline teeth 22P and 22S fitted into the spline grooves 23P3 and 23S3 only have to function as stoppers. For example, the spline grooves 23P3 and 23S3 have spline teeth 22P and 22S. You may comprise so that the movement of the movable sheaves 8 and 14 to the fixed sheaves 7 and 13 side may be prevented by forming the butting part which a tip part contacts. Further, the spline grooves 23P3 and 23S3 are formed to have the same groove width over the entire length thereof, and the thickness of the spline teeth 22P and 22S is tapered on the fixed sheaves 7 and 13 side, and the opposite side is spline groove 23P3. It is configured to be thicker than the groove width of 23S3. By doing so, when the movable sheaves 8 and 14 move to the fixed sheaves 7 and 13 side by a predetermined distance, the spline teeth 22P and 22S are engaged or fitted into the spline grooves 23P3 and 23S3, so that the fixed sheave 7 , 13 may be prevented from moving the movable sheaves 8, 14 to the side. Alternatively, the spline teeth 22P, 22S are provided with flange portions wider than the groove widths of the spline grooves 23P3, 23S3, and the flange portions are brought into contact with the end portions of the second spline teeth 23P, 23S to thereby fix the fixed sheave 7, The movable sheaves 8 and 14 may be prevented from moving toward the 13th side.

  DESCRIPTION OF SYMBOLS 1 ... Belt type continuously variable transmission, 2 ... Input shaft (drive side rotating shaft), 3 ... Primary pulley, 4 ... Output shaft (driven side rotating shaft), 5 ... Secondary pulley, 6 ... Belt, 7 ... First 1 fixed sheave, 8 ... second movable sheave, 13 ... second fixed sheave, 14 ... second movable sheave, 22P, 22S ... first spline teeth (spline teeth), 22P1, 22S1 ... one side surface of the first spline teeth (The other side of the spline teeth), 23P1, 23S1... One side of the second spline teeth (one side of the spline groove), 23P3, 23S3.

Claims (1)

A fixed sheave integrated with the rotating shaft; and spline teeth that fit into a spline groove formed along an axial direction of the rotating shaft on an outer peripheral surface of the rotating shaft, and the spline in the spline groove A pair of pulleys each having a movable sheave that rotates integrally with the rotary shaft and moves toward and away from the fixed sheave in the axial direction when the teeth are engaged, and is wound around the pair of pulleys. In a belt-type continuously variable transmission comprising a belt for transmitting torque between the pair of pulleys,
One of the two side surfaces of the spline groove is twisted with respect to the axial direction so that the groove width of the spline groove becomes narrower from the movable sheave side toward the fixed sheave side.
The other side surface of the both side surfaces of the spline teeth is opposed to the one side surface so that the tooth thickness of the spline teeth decreases from the side opposite to the fixed sheave toward the fixed sheave side, and Formed in parallel with the one side surface,
When the movable sheave moves to the fixed sheave side in the axial direction, the movement of the movable sheave is prevented by contacting the one side surface and the other side surface. A belt type continuously variable transmission.

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